CN102465726A

CN102465726A - Valve timing control apparatus

Info

Publication number: CN102465726A
Application number: CN2011102291760A
Authority: CN
Inventors: 加藤裕幸; 市野泽严典
Original assignee: Hitachi Automotive Systems Ltd
Current assignee: Hitachi Astemo Ltd
Priority date: 2010-10-29
Filing date: 2011-08-11
Publication date: 2012-05-23
Also published as: JP2012097594A; US20120103289A1

Abstract

A valve timing control apparatus includes a driving rotary member to receive a rotational force from a crankshaft of an engine, and a vane rotor connected with a camshaft and arranged to rotate relative to the driving rotary member, with at least one vane defining a retard pressure chamber and an advance pressure chamber in the inside of the driving rotary member. A lock member is received slidably in the vane of the vane rotor and arranged to engage with a lock hole when the vane is rotated to a predetermined angular position. The lock member includes forward and rearward end portions arranged to receive equal fluid pressures. The lock member further includes a pressure receiving portion to which an operating fluid pressure is selectively applied to force the lock member away from the lock hole.

Description

The Ventilsteuerzeitsteuervorrichtung of internal-combustion engine

Technical field

The present invention relates to according to the variable control intake valve of operating condition and exhaust valve is the Ventilsteuerzeitsteuervorrichtung of internal-combustion engine of the opening and close timing of internal combustion engine valve.

Background technique

As everyone knows; The Ventilsteuerzeitsteuervorrichtung that a kind of leaf type is arranged; Engage with the locking hole of the shell of being located at the driving side sprocket wheel to the axial lock pin that is provided with free to advance or retreatly through making in the blade of camshaft side; The relatively rotation place of blade is locked at the middle rotational position between maximum advancing angle side and the maximum retardation angle side, and locking keeps the valve timing of internal combustion engine valve thus.

In such Ventilsteuerzeitsteuervorrichtung; During engine starting; Before the hydraulic pressure that is sent to retardation angle hydraulic chamber or advancing angle hydraulic chamber by oil pump rises, keep the lockup state of blade, after hydraulic pressure rises, have to utilize the hydraulic pressure of same oil pump to keep the relieving state of locking.

So, keep or remove said lockup state through the hydraulic pressure of the other system different with the retardation angle hydraulic chamber with the advancing angle hydraulic chamber, the Ventilsteuerzeitsteuervorrichtung that obtains desirable control correct time etc. thus is documented in following patent documentation 1.

Patent documentation 1: (Japan) spy opens the 2003-222010 communique

But; The device of patent documentation 1 record is owing to the hydraulic pressure through other system makes the lock pin action; Therefore the external diameter of this lock pin divides large-diameter portion and two sections formation of minor diameter part, with hydraulic pressure supply of the step part between this large-diameter portion and minor diameter part or discharge selectively.Therefore, not only need guarantee the sliding of the slyness of lock pin, and need the axial two ends of this lock pin are opened to barometric pressure always.

Therefore; Have to strengthen the seal length of the circumferencial direction of blade; Be the length of the side seal between the inner surface of outer cover that slides of an axial end face and this end face of blade, in order to avoid the hydraulic pressure in said advancing angle hydraulic chamber or the retardation angle hydraulic chamber is from the part leakage of open to barometric pressure of the axial both end sides of lock pin.

Therefore, have to strengthen the breadth length of the circumferencial direction that forms said blade, there is the problem at the spinning movement angle that can not strengthen blade in its result.

Summary of the invention

The present invention proposes in view of the technical task of said existing technology; Its purpose is; A kind of Ventilsteuerzeitsteuervorrichtung of internal-combustion engine is provided, even the device that the hydraulic pressure through other system is advanced and retreat lock pin vertically, the big spinning movement angle that also can guarantee blade.

The invention of first aspect record is characterised in that: the basic comprising with rotary driving body, camshaft, advancing angle hydraulic chamber, retardation angle hydraulic chamber, lock pin and locking hole etc. is a prerequisite; Especially; Locking component forms; The compression area of advance and retreat direction both end sides is set at identical, and the same hydraulic pressure of the arbitrary hydraulic chamber in both end sides effect advancing angle hydraulic chamber and retardation angle hydraulic chamber, is provided with compression zone in the side of said locking component; Working hydraulic pressure is supplied with or is discharged to an end face side of this compression zone selectively, and the other end side is opened to barometric pressure via said vane rotor inside.

The invention of the 5th aspect record is characterised in that: especially; Has the first locking guiding groove; It extends and is provided with from march forward angular direction or retardation angle direction of first locking hole; Under the state that the front end of said first locking component snaps in, said vane rotor can rotate with respect to said rotary driving body relatively; Said first locking component forms; The compression area of advance and retreat direction both end sides is set at identical; And the same hydraulic pressure of the arbitrary hydraulic chamber in said advancing angle hydraulic chamber of said advance and retreat direction both end sides effect and retardation angle hydraulic chamber, and, compression zone be provided with in the side of first locking component; Working hydraulic pressure is supplied with or is discharged to an end face side of this compression zone selectively, and the other end side is opened to barometric pressure via said vane rotor inside.

The invention of eight aspect record is characterised in that: locking component forms; The compression area of advance and retreat direction both end sides is set at identical; And the same hydraulic pressure of the arbitrary hydraulic chamber in said advancing angle hydraulic chamber of said both end sides effect and retardation angle hydraulic chamber also is provided with the engaging release unit that makes said locking component engage selectively or break away from respect to said lock part.

According to the present invention, even the hydraulic pressure through other system makes the lock pin mobile device of advancing and retreat vertically, the big spinning movement angle that also can guarantee blade.

Description of drawings

Fig. 1 is the whole pie graph of first mode of execution of expression Ventilsteuerzeitsteuervorrichtung of the present invention;

Fig. 2 is the A-A line sectional drawing of Fig. 1 of the state of blade part that expression is used for this mode of execution rotational position that is maintained at intermediate phase;

Fig. 3 is the A-A line sectional drawing of Fig. 1 of blade part that expression is used for this mode of execution state that rotates to maximum retardation angle phase position;

Fig. 4 is the A-A line sectional drawing of Fig. 1 of blade part that expression is used for this mode of execution state that rotates to maximum advancing angle phase position;

Fig. 5 is the B-B line sectional drawing and the C-C line sectional drawing of Fig. 2 of action of each lock pin of this mode of execution of expression;

Fig. 6 is other the B-B line sectional drawing and the C-C line sectional drawing of Fig. 2 of action of each lock pin of this mode of execution of expression;

Fig. 7 is other the B-B line sectional drawing and the C-C line sectional drawing of Fig. 2 of action of each lock pin of this mode of execution of expression;

Fig. 8 is other the B-B line sectional drawing and the C-C line sectional drawing of Fig. 2 of action of each lock pin of this mode of execution of expression;

Fig. 9 is other the B-B line sectional drawing and the C-C line sectional drawing of Fig. 2 of action of each lock pin of this mode of execution of expression;

Figure 10 is other the B-B line sectional drawing and the C-C line sectional drawing of Fig. 2 of action of each lock pin of this mode of execution of expression.

Description of reference numerals

1 sprocket wheel

2 camshafts

3 phase places change mechanism

4 first oil hydraulic circuits

7 shells

The 7a housing main body

9 blade parts

10 wall parts

11 retardation angle hydraulic chambers

12 advancing angle hydraulic chambers

16a～16c blade

18 retardation angle oil path

19 advancing angles oil path

20 oil pumps

The 20a drain passageway

21 first electromagnetic switching valves

22 draining paths

24 first locking holes

24a, 24b, 24c first bottom surface, second bottom surface, the 3rd bottom surface (the first locking guiding groove)

25 second locking holes

25a, 25b first bottom surface, second bottom surface (the second locking guiding groove)

26 first lock pins

The 26a front end

The 26b rearward end

26c first compression zone

26e first compression face

27 second lock pins

The 27a front end

The 27b rearward end

27c second compression zone

27e second compression face

28 second oil hydraulic circuits

29,30 springs (force application part)

31a, 31b first pin-and-hole, second pin-and-hole

32,33 first releasings are removed with compression chamber, second and are used compression chamber

34 row's of confession paths

36 second electromagnetic switching valves

37 path formation portions

43,44 spiracles

Oilhole before and after 45a, the 45b

Oilhole before and after 46a, the 46b

Embodiment

Below, based on description of drawings the Ventilsteuerzeitsteuervorrichtung of the internal-combustion engine that the present invention relates to is applied to the for example mode of execution of the air inlet reveal of motor vehicle driven by mixed power, idling stop vehicle etc.

Like Fig. 1～shown in Figure 4, Ventilsteuerzeitsteuervorrichtung of the present invention has: the rotary driving body is a sprocket wheel 1, and its bent axle through internal-combustion engine is rotated driving via timing chain; The camshaft 2 of air inlet side, it is provided with along the configuration of internal-combustion engine fore-and-aft direction and with respect to said sprocket wheel 1 rotatably; Phase place change mechanism 3, it is configured between said sprocket wheel 1 and the camshaft 2, conversion these both relatively rotate phase place; First oil hydraulic circuit 4, it makes this phase place change mechanism 3 actions.

Said sprocket wheel 1 forms that roughly heavy wall is discoideus; Has the gear part 5 that is wound with said timing chain on the periphery; And said sprocket wheel 1 constitutes as the back cover of the open rearward end of stating shell after stopping up; Connect and be formed with support holes 6 in central authorities, this support holes 6 be rotatably freely supported on be fixed on said camshaft 2 after state on the periphery of vane rotor.

Said camshaft 2 is bearing on the not shown cylinder head via the camshaft bearing rotation freely; Being fixed with integratedly in the axial position of outer circumferential face and making internal combustion engine valve is a plurality of cams that intake valve starts work, and at one end is formed with female threaded hole 2a on the internal axis direction of portion.

Like Fig. 1 and shown in Figure 2, said phase place changes mechanism 3 to be had: shell 7, and it is along axially being located at integratedly on the said sprocket wheel 1; Driven solid of rotation is a blade part 9, and it is fixed via the cam bolt 8 with the female threaded hole 2a threaded joint of an end of said camshaft 2, and rotation is housed in the said housing 7 freely; Each retardation angle hydraulic chamber 11 and advancing angle hydraulic chamber 12 of three, it is that wall part 10 separates with blade part 9 and is formed in the said shell 7 by three shoe plates (シユ one) that the inner peripheral surface of this shell 7 had.

Said shell 7 forms and stops up the front shroud 13 of the front opening of said housing main body 7a by the housing main body 7a cylindraceous of sintering metal system, through impact briquetting, the said sprocket wheel 1 as back cover of obstruction open rearward end constitutes.Three bolts 14 of housing main body 7a, front shroud 13 and chain wheel body 5 each the bolt insertion hole 10a through connecting each said wall part 10 are tightened jointly and are fixed.Connect and be formed with inserting hole 13a in the central authorities of said front shroud 13.

Said blade part 9 forms through metallic material, by the vane rotor 15 of an end that is fixed on camshaft 2 through cam bolt 8 and the outer circumferential face of this vane rotor 15 along the circumferential direction roughly 120 ° of radial three blade 16a～16c that are provided with highlightedly in equally spaced position constitute.

Said vane rotor 15 forms the roughly cylindric of fore-and-aft direction length; The sealed member cylindraceous that is provided with the step path of thin-walled in the substantial middle position of front-end face 15b integratedly inserts guide portion 15a, and rearward end 15c extends and is provided with towards camshaft 2 directions.In addition, be formed with columned telescoping groove 15d in inside from the front end of said vane rotor 15 to rearward end.

On the other hand; Said blade 16a～16c is configured in respectively between each wall part 10; And the breadth of circumferencial direction has nothing in common with each other, and the blade 16a of maximum breadth and the blade 16b of middle equal-amplitude surface form roughly fan-shaped, and the blade 16c of minimum breadth to form heavy wall tabular.At the outer circumferential face of each said blade 16a～16c and the front end of wall part 10, be respectively equipped with the internal surface of can main body 7a and sealed member 17a, the 17b between the vane rotor outer circumferential face.

In addition; As shown in Figure 3; If said blade part 9 rotates to the retardation angle side relatively, the side 16d of then maximum breadth blade 16a be formed on the raised face (RF) 10b butt of the opposite side in an opposed said next door 10, limit the rotational position of maximum retardation angle side; As shown in Figure 4; The angle side is rotated relatively if said blade part 9 marches forward, and the raised face (RF) 10c butt in the another side 16e of then maximum breadth blade 16a and opposed another next door 10 limits the rotational position of maximum advancing angle side.

At this moment, with regard to

other blade

16b, 16c, bi-side not with circumferencial direction on the opposed faces butt in opposed each next door 10, be in separated state.Therefore, the butt precision in blade part 9 and next door 10 improves, and each

hydraulic chamber

11,12 of stating backward supplies with speeding up of hydraulic pressure, thereby the positive and negative rotation responsiveness of blade part 9 improves.

Between the bi-side of the bi-side of the positive and reverse return veer of each said blade 16a～16c and each wall part 10; Separating has described each retardation angle hydraulic chamber 11 and each advancing angle hydraulic chamber 12, and each retardation angle hydraulic chamber 11 is communicated with said first oil hydraulic circuit 4 via the first intercommunicating pore 11a and the second intercommunicating pore 12a that the general radial in the inside of said vane rotor 15 forms respectively with each advancing angle hydraulic chamber 12.

Working oil (hydraulic pressure) is supplied with or discharged to said first oil hydraulic circuit 4 to each said retardation angle hydraulic chamber 11, each said advancing angle hydraulic chamber 12 selectively; As shown in Figure 1, said first oil hydraulic circuit 4 has: via the first access 11a to each retardation angle hydraulic chamber 11 supply with or discharge hydraulic pressure retardation angle oil path 18, via the second access 12a to each advancing angle hydraulic chamber 12 supply with or discharge the advancing angle oil path 19 of hydraulic pressure, the hydrodynamic pressure supply source of supplying with working oil to this each

path

18,19 selectively is oil pump 20, switch first electromagnetic switching valve 21 of the stream of said retardation angle oil path 18 and said advancing angle oil path 19 according to the internal combustion engine operation state.Said oil pump 20 is the common oil pumps such as trochoid pump through the crankshaft rotating driving of internal-combustion engine.

Said retardation angle oil path 18 is connected with the via hole of said first electromagnetic switching valve 21 with said advancing angle oil path 19 end separately; And the other end is communicated with each said retardation angle hydraulic chamber 11 and each said advancing angle hydraulic chamber 12 via

passage portion

18a, 19a and said first,

second access

11a, 12a respectively; Wherein,

passage portion

18a, 19a are formed on abreast vertically and insert inside and said sealed member logical and that remain in the vane rotor 15 of said blade part 9 and insert in the roughly columned path formation portion 37 in the guide portion 15a.

Said path formation portion 37 is fixed on through the end that makes its outside and constitutes non-rotary part on the not shown chain guard; Except that each said

passage portion

18a, 19a, within it portion axially on also be formed with the path of second oil hydraulic circuit 28 of the locking of the lockable mechanism of stating after the releasing.

As shown in Figure 1; Said first electromagnetic switching valve 21 is the Proportional valve of three of four-holes; Through not shown electronic controller, make the not shown slide valve that in valve body, is provided with sliding freely vertically, move along fore-and-aft direction; So that the drain passageway 20a of oil pump 20 is communicated with any said

oily path

18,19, this another

oily path

18,19 and draining path 22 are communicated with.In addition, under the situation when internal-combustion engine stops etc., said slide valve remains on axial middle mobile position, blocks the connection of said

oily path

18,19 and drain passageway 20a, draining path 22 fully, and working oil is sealed in each

hydraulic chamber

11,12.

The suction path 20b of oil pump 20 and draining path 22 are communicated with in oil pump 23.In addition, the main oil gallery M/G to the supplies such as slide part of internal-combustion engine is communicated with the downstream side of the said drain passageway 20a of oil pump 20 with lubricant oil, and is provided with filter 50 in this downstream side.Oil pump 20 also is provided with flow control valve 51, and the working oil of the surplus that this flow control valve 51 will be discharged from drain passageway 20a is discharged to oil pump 23, thereby controls suitable flow.

With regard to said electronic controller; Inner computer input is from not shown crank angle sensor (detection internal-combustion engine rotational speed), Air flow meter, internal-combustion engine cooling-water temperature sensor, engine temperature sensor, engine load sensor and the information signal that detects the various sensors such as cam angle sensor of the current rotatable phase of camshaft 2; Detect current internal combustion engine operation state; Simultaneously; To first electromagnetic switching valve 21 and after each electromagnetic coil output control pulse electric current of second electromagnetic switching valve 36 stated, the mobile position of control slide valve separately, thereby each said path of switching controls.

And; In this mode of execution, be provided with position holding device, this position holding device remains on blade part 9 the middle rotatable phase position (position of Fig. 2) between the rotational position (position of Fig. 4) of rotational position (position of Fig. 3) and maximum advancing angle side of maximum retardation angle side with respect to shell 7.

Like Fig. 5～shown in Figure 10, the main composition of this position holding device will have: cross section roughly two locking hole component parts 1a, the 1b of T shape of assigned position that is located at the circumferencial direction of said sprocket wheel 1 inner side surface; Be respectively formed at this locking hole component parts 1a, the last lock part of 1b is first,

second locking hole

24,25; Be located at said blade part 9 two

blade

16a, 16b inside and engage with each said locking

hole

24,25 respectively or two locking components breaking away from are first,

second lock pin

26,27; Remove said second oil hydraulic circuit 28 (with reference to Fig. 1) of this each

lock pin

26,27 with respect to the engaging of each said locking hole 24,25.Need to prove that this second oil hydraulic circuit 28 constitutes one of engaging release unit.

Like Fig. 2～shown in Figure 5; Said each locking hole 24 forms the circular arc slotted hole shape (silkworm shape) that extends along the circumferencial direction of sprocket wheel 1, and the rotational position of maximum retardation angle side of said blade part 9 of inner side surface 1c that is formed on relative sprocket wheel 1 is near the neutral position of advancing angle side.In addition, first locking hole 24 forms the step-like of its bottom surface three sections from the retardation angle side to advancing angle side step-down successively, and this becomes the first locking guiding groove.

Promptly; Like Fig. 5～shown in Figure 10; The inner side surface 1c that the first locking guiding groove forms sprocket wheel 1 is made as epimere; One section one section ground step-down and form the step-like of the first bottom surface 24a, the second bottom surface 24b, the 3rd bottom surface 24c successively thus, the inner side surface 24d of retardation angle hydraulic chamber 11 sides becomes the wall of vertically holding up.Therefore; If the front end 26a of first lock pin 26 that engages with each said bottom surface 24a～24c successively interimly descends mobilely from the interior edge face 1c of sprocket wheel 1 through each bottom surface 24a～24c angular direction of marching forward via blade 16a, then rightabout the moving of each step surface restriction is moving of retardation angle direction.Thereby each bottom surface 24a～24c plays a role as overrunning clutch (ratchet).

Said first lock pin 26 is connected to the time point of said inner side surface 24d at the lateral margin of its front end 26a, and the angular direction that is limited to march forward (retardation angle hydraulic chamber 11 sides) move (with reference to Figure 10).

Like Fig. 2～shown in Figure 5; Said second locking hole 25 is identical with first locking hole 24; Form the slotted hole shape that extends along the circumferencial direction of sprocket wheel 1, and the rotational position of maximum retardation angle side of said blade part 9 of inner side surface 1c that is formed on relative sprocket wheel 1 is near the neutral position of advancing angle side.In addition, this second locking hole 25 forms the step-like of its bottom surface two sections from advancing angle hydraulic chamber 12 sides to retardation angle hydraulic chamber 11 sides step-down successively, and this becomes the second locking guiding groove.

That is, the inner side surface 1c that this second locking hole 25 forms sprocket wheel 1 is made as epimere, and the first bottom surface 25a, the second bottom surface 25b be step-down step-like successively, and the inner side surface 25c of retardation angle hydraulic chamber 11 sides becomes the wall of vertically holding up.In addition; The degree of depth of the first bottom surface 25a forms darker a little than the first bottom surface 24a of first locking hole via step surface; The degree of depth of the second bottom surface 25b is set at the big degree of depth with the degree of depth addition of the second bottom surface 24b and the 3rd bottom surface 24c via step surface 25c, and the whole degree of depth is set at the roughly the same degree of depth of the 3rd bottom surface 24c with said first locking hole 24.Therefore; Interimly descend mobilely via blade 16a through each

bottom surface

25a, 25b angle side of marching forward if be fastened on the front end 27a of second lock pin 27 of each said

bottom surface

25a, 25b, then rightabout the moving of each step surface restriction is moving of maximum retardation angle direction.Thereby each

bottom surface

25a, 25b play a role as overrunning clutch (ratchet).

And said second lock pin 26 is connected to the time point of the step surface 25c of the second bottom surface 25b at the lateral margin of its front end 26a, is limited to move (with reference to Figure 10) to retardation angle direction (advancing angle hydraulic chamber 12 sides).

And; The relation of the relative formation position of first,

second locking hole

24,25 such as Fig. 5～shown in Figure 10; At first lock pin 26 butt successively and be sticked in stage of first of first locking hole 24～the 3rd bottom surface 24a～24c; Like Fig. 5～shown in Figure 8, the front-end face that second lock pin 27 is in front end 27a still also is connected to the state of the inner side surface 5d of chain wheel body 5.

Thereafter; Like Fig. 9 and shown in Figure 10; Set relative position according to following mode: at the front end of first lock pin 26 through march forward a little time point of angle side shifting of the 3rd bottom surface 24c; The front end 27a ability butt of second lock pin 27 also is sticked in the first bottom surface 25a; With the state that is sticked in the 3rd bottom surface 24c and then the angle side shifting and be connected to the time point of inner side surface 24d of marching forward, the front end 27a butt of second lock pin 27 also is fastened on the second bottom surface 25b and lateral margin is connected to step surface 25c at first lock pin 26.

In a word; Along with blade part 9 rotates to the advancing angle side position relatively from the retardation angle side position of stipulating; Said first lock pin 26 interim successively ground butt also is fastened on the first bottom surface 24a～the 3rd bottom surface 24c; Then, second lock pin 27 interim successively ground butt and be fastened on the first bottom surface 25a and the second bottom surface 25b.Thus, be the ratchet effect of five steps through integral body, Yi Bian blade part 9 is limited the rotation to the retardation angle direction,, finally remain on the intermediate phase position between maximum retardation angle phase place and the maximum advancing angle phase place Yi Bian the angular direction of marching forward rotates relatively.

Shown in Fig. 1, Fig. 5 etc.; Said first lock pin 26 is configured in sliding freely and connects vertically and be formed in the first pin-and-hole 31a of inside of maximum breadth blade 16a; The external diameter of said first lock pin 26 forms step footpath shape, by the middle footpath 26b of portion of the rear portion side of the said front end 26a of path, this front end 26a, outer circumferential face of the rear end side of the 26b of footpath portion forms for the first flange shape compression zone 26c greatly directly in this.

The front end 26a side of the 26b of footpath portion is thickly slided at the inner peripheral surface liquid of sleeve 40 that is pressed into and be fixed in the forward end of the said first pin-and-hole 31a in said, and rearward end 26d liquid in the first pin-and-hole 31a thickly slides.The front-end face of said front end 26a form can be with each bottom surface 24a～24c butt of tightlock status and said first locking hole 24 smooth planar.

In addition, through in the rear end side of the 26b of footpath portion therefrom along the i.e. spring force of first spring 29 of the inner shaft force application part that elasticity is installed between the internal surface of groove floor that forms and front shroud 13, this first lock pin 26 is stressed to the direction that is sticked in first locking hole 24.

In addition, on the front end 26a and rearward end 26d of this first lock pin 26, via the oilhole 45a of the front and back that are formed at said

blade

16a, 45b effect same hydraulic pressure from said advancing angle hydraulic chamber 12.Promptly; The compression area of bottom surface 26i addition of ear end face 26h and spring groove of compression area and the rearward end 26d that faces another said oilhole 45b of front-end face 26f and the ring-type front-end face 26g addition of the middle footpath 26b of portion that faces the said front end 26a of a said oilhole 45a is set to identical, and they are acted on the same hydraulic pressure of advancing angle hydraulic chamber 12 respectively simultaneously.

In addition, the said first compression zone 26c constitute state after the lower end surface faces among the figure first remove compression chamber 32 the first compression face 26e, and the upper-end surface via the spiracle 43 that forms connected state in and the front shroud 13 inner at said blade 16a to atmosphere opening.

Said second lock pin 27 be configured in sliding freely along in the second pin-and-hole 31b that forms to perforation of the inner shaft of equal-amplitude surface blade 16b; Identical with first lock pin 26; The external diameter of said second lock pin 27 forms step footpath shape, by the middle footpath 27b of portion of the rear portion side of the said front end 27a of path, this front end 27a, outer circumferential face of the rear end side of the 26b of footpath portion forms for the second flange shape compression zone 27c greatly directly in this.In addition, said in the front end 27a side of the 27b of footpath portion be pressed into and be fixed in that liquid thickly slides in the inner peripheral surface of sleeve 41 of forward end of the said second pin-and-hole 31b, and rearward end 27d liquid in the second pin-and-hole 31b thickly slides.The front-end face of said front end 27a form can be with each bottom surface 25a of tightlock status and said

second locking hole

25,25b butt smooth planar.

In addition, through in the rear end side of the 27b of footpath portion therefrom along the i.e. spring force of second spring 30 of the inner shaft force application part that elasticity is installed between the internal surface of groove floor that forms and front shroud 13, this second lock pin 27 is stressed to the direction that is sticked in second locking hole 25.

In addition, on the front end 27a and rearward end 27d of this second lock pin 27, via the oilhole 46a of the front and back that are formed at said

blade

16b, 46b effect same hydraulic pressure from said advancing angle hydraulic chamber 12.Promptly; The compression area of bottom surface 27i addition of ear end face 27h and spring groove of compression area and the rearward end 27d that faces another said oilhole 46b of front-end face 27f and the ring-type front-end face 27g addition of the middle footpath 27b of portion that faces the said front end 27a of a said oilhole 46a is set to identical, and they are acted on the same hydraulic pressure of advancing angle hydraulic chamber 12 respectively simultaneously.

And, the said second compression zone 27c constitute state after the lower end surface faces among the figure second remove compression face 33 the second compression face 27e, and the upper-end surface via across said blade 16b inner with front shroud 13 in and the spiracle 44 of formation to atmosphere opening.

Like Fig. 1 and shown in Figure 5, said second oil hydraulic circuit 28 has: be formed on said first between the first compression zone 26c of big footpath stepped part and first lock pin 26 of the said first pin-and-hole 31a and remove with compression chamber 32; Being formed on said second between the second compression zone 27b of big footpath stepped part and second lock pin 27 of the second pin-and-hole 31b removes with compression chamber 33; First, second is removed with

compression chamber

32,33, supply with hydraulic pressure, via supply drain passageway 34 from the drain passageway 35b discharge working oil of said draining path 22 branches via supply passage 35a from the drain passageway 20a branch of said oil pump 20; Second control valve that switches said supply drain passageway 34 and each

path

35a, 35b according to the state of internal-combustion engine selectively is said second electromagnetic switching valve 36.

Said first releasing is removed with compression chamber 33 supplying to inner hydraulic pressure respectively in said first,

second compression face

26e, 27e with compression chamber 32 and said second; So that first,

second lock pin

26,27 overcomes the spring force of each

spring

29,30; Retreat from first,

second locking hole

24,25, thereby remove engaging separately.

The via hole of one distolateral and corresponding said second electromagnetic switching valve 36 of said supply drain passageway 34 connects; And another distolateral supply drain passageway 34a of portion of branch from the inner shaft of said path formation portion 37 to crooked to radially, first, second the oily via hole 38a, the 38b that form via branch in said vane rotor 15 respectively are communicated with

compression chamber

32,33 with each said first, second releasing.

And; Front and back position vertically at the outer circumferential face of said path formation portion 37 is formed with circular a plurality of embedding slots; And; Setting-in and be fixed with three annular seal parts 39 respectively in this each embedding slot, these sealed members sealings 39 sealing each said

passage portion

18a, 19a and be formed on first and supply with between each opening end of support holes 15d side of drain passageway 34a etc.

Said second electromagnetic switching valve 36 is the Proportional valve of three of four-holes; Through spring force from the control electric current of the on-off of said electronic controller output or inner valve spring; Suitably optionally be communicated with said supply drain passageway 34 and said

path

35a, 35b by slide valve; And the connection of drain passageway 34 and each

path

35a, 35b is supplied with in blocking-up, and working oil is sealed in each said releasing with in the

compression chamber

32,33.

Below, the effect to this mode of execution describes based on accompanying drawing.

(the action control after the short time stops)

At first, after normal vehicle operation, close ignition switch when internal-combustion engine is stopped, the driving of oil pump 20 also stops; Therefore stop to supply with working oil to any

hydraulic chamber

11,12, and, allow blade part 9 positive and negative rotating freely; Therefore; Under the cam torque situation of correct time for negative torque of the alternately torque when internal-combustion engine stops, the angular direction rotation of marching forward can not remain on maximum retardation angle phase place; Therefore, carry out that internal-combustion engine stops control so that said cam torque becomes positive torque correct time when internal-combustion engine stops.

At this moment, to the energising of first electromagnetic switching valve 21, the slide valve retentive control in the neutral position, is blocked each

path

18,19 and each

path

20a, 22 connection by said electronic controller.

That is, if the driving of oil pump 20 stops, the working oil in the then said drain passageway 20a turns back in the oil sump 23 from oil pump 20 through the lift difference, and the working oil in each

hydraulic chamber

11,12 also might flow down.If do not have working oil in each

hydraulic chamber

11,12, the blade part 9 that then is positioned at maximum retardation angle side is uneven when the engine starting because of said alternately torque, and this imbalance causes producing between said blade part 9 and the next door 10 clashes into noise.

So, in this mode of execution, control first electromagnetic switching valve 21, close each

path

18,19, seal operation is oily in each

hydraulic chamber

11,12, can fully prevent the imbalance of said blade part 9 thus.

Thereafter; Maintaining heat machine state through for example 15 minutes with the interior short time after; If cranking internal combustion engine once more, then at this time point, blade part 9 remains on the rotatable phase position of maximum retardation angle side shown in Figure 3; The period of closing of intake valve, relative piston lower dead centre was near maximum retardation angle side, so effective compression ratio descends.Thus, pumping loss reduces, and has suppressed vibration, has obtained good startability.

In addition; The switching manipulation of said ignition switch is not depended in control after the said short time of process, and during self-braking idling stops to wait in vehicle driving, because the time from stopping to starting is short; Therefore carry out foregoing action control; Said blade part 9 is remained on the rotational position of maximum retardation angle side, so the effective compression ratio of the internal-combustion engine when obtaining restarting descends identical action effect such as startability is good.

(through the action control after long-time)

In addition; Stopping internal-combustion engine and through behind long-time more than 15 minutes for example; Being internal-combustion engine is undertaken by starting motor under the situation that the rotation of bent axle begins opening ignition switch under the state of low temperature, through electronic controller slide valve vertically direction in first electromagnetic switching valve 21 is moved, and drain passageway 20a and retardation angle oil path 18 and a side in the oily path 19 of advancing angle are communicated with; And, draining path 22 is communicated with the opposing party in the said

oily path

18,19.

Simultaneously, to 36 energisings of second electromagnetic switching valve, make and supply with drain passageway 34 and drain passageway 35b connection.Thus, first, second is removed with the working oil in the

compression chamber

32,33 and is discharged from, and through the spring force of each

spring

29,30, each

lock pin

26,27 is stressed to turnover direction (being sticked in the direction of locking hole 24,25).

Carry out initial stage of crankshaft rotating at this by starting motor, because the discharge hydraulic pressure of said oil pump 20 still is in low pressure, therefore the hydraulic pressure in any hydraulic chamber in the said

hydraulic chamber

18,19 does not rise.

Therefore; Through the said alternately torque that acts on camshaft 2, especially negative torque; Like Fig. 5 and shown in Figure 6, the blade part 9 angle sideway swivel of marching forward slightly, the front end 26a butt of said first lock pin 26 also is fastened on the first bottom surface 24a of first locking hole 24.At this time point, to the positive torque of blade part 9 effects, thereby it is to the retardation angle sideway swivel, but the lateral margin of the front end 26a of first lock pin 26 is connected to the step surface of holding up of the first bottom surface 24a, and has limited the rotation to the retardation angle side.

Thereafter; According to negative torque; The blade part 9 angle sideway swivel of marching forward, first lock pin 26 moves with the mode that reduces step successively like Fig. 7～shown in Figure 9 thereupon, and butt also is fastened on the second bottom surface 24b, the 3rd bottom surface 24c; And, while moved by the ratchet effect angular direction of marching forward through the 3rd bottom surface 24c.Meanwhile, like Fig. 9 and shown in Figure 10, while second contract shotpin 27 front end 27a receive ratchet effect butt and be fastened on the first bottom surface 25a, the second bottom surface 25b of second locking hole 25 successively, finally be stuck and keep in 25b position, second bottom surface.

Shown in figure 10; The lateral margin butt of the front end 26a of first lock pin 26 of this time point and remain on the said inner side surface 24d of the advancing angle direction (retardation angle hydraulic chamber 11 sides) of holding up from the 3rd bottom surface 24c; On the other hand; The lateral margin of the front end 27a of second lock pin 27 is connected to the said inner side surface 25c of advancing angle hydraulic chamber 12 sides of holding up from the second bottom surface 25b, thereby first lock pin 26 and second lock pin 27 stably keep respectively.

As shown in Figure 2, through this action, blade part 9 remains on the intermediate phase position, and the valve-closing time of intake valve is controlled at the forward advancing angle side of relative piston lower dead centre.Therefore, the compression ratio of internal-combustion engine improves, and burning is good, and the startability during cold starting etc. improves.

In addition, be in for example high rotary area if forward the normal operation after the hot machine of internal-combustion engine finishes to, then first electromagnetic switching valve 21 is communicated with drain passageway 20a and advancing angle oil path 19, and retardation angle hydraulic chamber 18 and draining path 22 are communicated with.

Thus, each retardation angle hydraulic chamber 11 becomes low pressure, and each advancing angle hydraulic chamber 12 becomes high pressure, and therefore as shown in Figure 4, said blade part 9 moves to maximum advancing angle sideway swivel.Thus, the ETAD expected time of arrival and departure of intake valve shifts to an earlier date, and with the valve overlap duration increasing of exhaust valve, sucking air quantity increases, the output raising.

As previously mentioned, at this time point, second electromagnetic switching valve 36 makes supplies with drain passageway 34 and supply passage 35a connection, hydraulic pressure is supplied with to each

compression chamber

32,33, and drain passageway 35b is kept closed condition, therefore, has guaranteed rotating freely of blade part 9.

As stated, in this mode of execution, be the temperature of internal-combustion engine according to the stop time of internal-combustion engine; The compression ratio of internal-combustion engine of change when restarting, therefore, the reducing of the torque load in the time of can be through starting etc.; Improve startability, reduced vibration, and improved gas exhausting property.

In addition; Owing to improved the performance that blade part 9 is remained on the intermediate phase position through position holding device; And; Each bottom surface 24a～24c, 25a, the 25b of the step-like locking guiding groove through each locking

hole

24,25, each

lock pin

26,27 is inevitable only to be directed moving to each locking

hole

24,25 direction, therefore can guarantee the reliability and stability of this leading role.

In addition; Owing to use the hydraulic pressure of the other system different as the hydraulic pressure that acts on each said

compression chamber

32,33 with the hydraulic pressure of each said

hydraulic chamber

11,12; So compare with the situation of the hydraulic pressure that uses each

hydraulic chamber

11,12; Responsiveness to each said

compression chamber

32,33 is supplied with hydraulic pressure is good, and the mobile responsiveness of retreating of each

lock pin

26,27 improves.In addition, sealing mechanism that no longer need be from each

hydraulic chamber

11,12 to 32,33 of each compression chambers.

And; In this mode of execution,, spiracle is set unlike the such axial both end sides of present technology at each

lock pin

26,27 for the level and smooth advance and retreat that obtain each

lock pin

26,27 move; But the axial both end sides of each said

lock pin

26,27 is communicated with said advancing angle hydraulic chamber 12 via each

oilhole

45a, 45b; Act on same hydraulic pressure in each

lock pin

26,27 front and back separately, average out in the axial direction thus, therefore; Utilize the spring force of each said

spring

29,30 and remove the pressure reduction of the hydraulic pressure of

compression chamber

32,33 supplies, each

lock pin

26,27 advance and retreat is moved to said first, second.

In other words; Be not provided for guaranteeing the spiracle of the rapid sliding of each lock pin 2,27 at said locking

hole component parts

1a, 1b; And act on the same hydraulic pressure of said advancing angle hydraulic chamber 12 in the front and back of each

lock pin

26,27, make each

lock pin

26,27 balance in the axial direction thus, thereby obtain the effect identical with spiracle; Therefore, can reduce sideshake between each opposed faces of axial both ends of the surface and front shroud 13 and sprocket wheel 1 of maximum breadth blade 16a.

Thus, can must be shorter than present with the shorten length of the circumferencial direction of maximum breadth blade 16a.Consequently; Can strengthen the rotation angle range of the circumferencial direction under the relativeness of

opposed faces

10b, 10c of side and opposed

wall part

10,10 of circumferencial direction of this maximum breadth blade 16a; Therefore, can strengthen the relatively rotate phase angle of blade part 9 with respect to said shell 7.

Need to prove; Said each

spiracle

43,44 with upper-end surface side direction atmosphere opening each compression face 26e, the opposite side of 27e said each

compression zone

26c, 27c is formed in the inside and front shroud 13 of each

blade

16a, 16b; All be not communicated with said advancing angle hydraulic chamber 12; Therefore, can not leak working oil thus.

Owing to the hydraulic pressure in the advancing angle hydraulic chamber 12 is supplied with to the axial two ends of said

lock pin

26,27, so can seek the stabilization of the action of each lock pin 26,27.Promptly; Sometimes when engine starting, in the working oil that said retardation angle hydraulic chamber 11 is supplied with, sneaked into air; If will sneak into the working oil of air supplies with to the two ends of

lock pin

26,27; The air of then sneaking into said hydraulic pressure makes the action of

lock pin

26,27 unstable, and whop etc. might take place.

But, almost there is not air to sneak in the hydraulic pressure that the angle hydraulic chamber 12 of marching forward in the normal operation behind engine starting is supplied with, therefore, the action of said

lock pin

26,27 is stable, can suppress the generation of whop etc.

In addition; The step of first, second bottom surface 25a through improving the second locking guiding groove, the hypomere of 25b; Near the intensity of said step surface 25c that constitutes second locking hole 25 is improved; Therefore, be connected to step surface 25c repeatedly, also can seek to improve its durability even be sticked in the lateral margin of second lock pin 27 of second locking hole 25.

On the other hand, be sticked under the situation of first locking hole 24 at first lock pin 26, the lateral margin of front end 26a is connected to the big said inner side surface 24d of area of the second the darkest bottom surface 24c, therefore, from this point, also can seek to improve durability.

In addition, through said first, second locking guiding groove is formed the silkworm shape respectively, can access the level and smooth rotary action of first,

second lock pin

26,27 that rotates along with the rotation of blade part 9.

And; In this mode of execution, will from internal-combustion engine stop to the transit time of restarting as parameter, but whether with the transit time as parameter; But directly will control as parameter from the temperature information of engine temperature sensor; Also can be divided into below the set point of temperature and the above control action of set point of temperature, therefore, the method for this moment is very practical.

In addition; In this mode of execution; Position holding device is divided into first lock pin 26 and first～the 3rd bottom surface 24a～24c and first lock pin 27 forms with first, second bottom surface 25a, two parts of 25b, can reduces to form the wall thickness of the said sprocket wheel 1 of each locking

hole

24,25 thus.That is, for example in that to establish lock pin be single and form continuously under the situation of each step-like bottom surface 24a～24c, 25a, 25b, in order to ensure this step-like height; Must thicken the wall thickness of said chain wheel body 5, but as previously mentioned, through being divided into two parts; Can reduce the wall thickness of chain wheel body 5; Therefore, can shorten the axial length of Ventilsteuerzeitsteuervorrichtung, improve degree of freedom in design.

In addition, each said

lock pin

26,27 is formed cylindric, and the flange through simple shape

forms compression zone

26c, 27c, and therefore,

lock pin

26,27 whole manufacturing operations become easily, can suppress the rising of cost.

The present invention is not limited to the formation of said mode of execution, and Ventilsteuerzeitsteuervorrichtung not only is applied to the air inlet side, can also be applied to exhaust side.

Below, explain from the technological thought of the invention except that the scope that requires to protect of said mode of execution grasp.

(invention a) is characterized in that, invent in the Ventilsteuerzeitsteuervorrichtung of the internal-combustion engine of being put down in writing in first aspect,

Said locking component is made up of the lock pin that the side in cylindrical body is provided with the lip part of the toroidal that constitutes said compression zone.

Owing to main body is formed cylindric, and the flange through simple shape forms compression zone, so the manufacturing operation of lock pin integral body becomes easily, can suppress the rising of cost.

(invention b) is characterized in that, invent in the Ventilsteuerzeitsteuervorrichtung of the internal-combustion engine of being put down in writing in first aspect,

Said rotary driving body has: shell cylindraceous, and its axial at least end forms opening, is provided with shoe plate highlightedly at inner peripheral surface; Sealing plate, it seals the opening end of this shell, and is formed with opening portion in the periphery of said relatively blade near radially inner side,

Inside in the axial end face side of said blade forms the intercommunicating pore that an end is communicated with said opening portion, through this intercommunicating pore, with the other end side direction atmosphere opening of said compression zone.

(invention c) is characterized in that, invent in the Ventilsteuerzeitsteuervorrichtung of the internal-combustion engine of being put down in writing in first aspect,

Supply with the hydraulic pressure of the other system different with the pressure of said advancing angle hydraulic chamber or retardation angle hydraulic chamber in an end face side of said compression zone.

According to the present invention; Because the hydraulic pressure that uses the system different with the hydraulic pressure of each said hydraulic chamber is pressed in the work as an end face side that acts on compression zone; So compare with the situation of the hydraulic pressure that uses each hydraulic chamber; Responsiveness to said compression zone supply work is pressed is good, and does not need the sealing of each one.

(invention d) is characterized in that, in the Ventilsteuerzeitsteuervorrichtung of the invention internal-combustion engine that c put down in writing,

Have: first control valve that hydraulic pressure is supplied with or discharged to said advancing angle hydraulic chamber or retardation angle hydraulic chamber selectively, second control valve that hydraulic pressure is supplied with or discharged to an end face side of said compression zone.

(invention e) is characterized in that, in the Ventilsteuerzeitsteuervorrichtung of the invention internal-combustion engine that d put down in writing,

Said first control valve is made up of proportional control valve,

Said second control valve is made up of the control valve that is controlled at two positions selectively.

(invention f) is characterized in that, invent in the Ventilsteuerzeitsteuervorrichtung of the internal-combustion engine of being put down in writing in first aspect,

Advance and retreat direction two ends at said locking component act on the hydraulic pressure in the said advancing angle hydraulic chamber.

Because at the advance and retreat direction two ends of locking component, the hydraulic pressure of advancing angle hydraulic chamber is simultaneously with the pressure effect, so said locking component is in state of equilibrium, advanced and retreat mobile rapidly according to the difference of the active force of hydraulic pressure that acts on said compression zone and force application part.

And, owing to supply with the hydraulic pressure in the advancing angle hydraulic chamber at the two ends of said locking component, so can seek the stabilization of the action of locking component.That is, in the working oil that said retardation angle hydraulic chamber is supplied with, supply with to the two ends of locking component when air is sneaked into engine starting sometimes if will sneak into the working oil of air; The air of then sneaking into said hydraulic pressure makes the action of locking component unstable; Whop etc. might take place, still, owing to almost do not have air to sneak in the hydraulic pressure that the angle hydraulic chamber that marches forward in the normal operation behind engine starting is supplied with; So the action of said locking component is stable, can suppress to hit the generation of sound etc.

(invention g) is characterized in that, invent in the Ventilsteuerzeitsteuervorrichtung of the internal-combustion engine of being put down in writing in second aspect,

In the bottom surface of the said first locking guiding groove, be provided with step-like step towards said first locking hole.

(invention h) is characterized in that, invent in the Ventilsteuerzeitsteuervorrichtung of the internal-combustion engine of being put down in writing in second aspect,

On said vane rotor, be provided with a plurality of said blades,

In the blade different with the said blade that is provided with said first locking component, be provided with second locking component vertically free to advance or retreatly,

And have: second locking hole; The front end of said second locking component can or break away from the engaging of this second locking hole, and this second locking hole is arranged on the position that the front end of said second locking component when said blade rotates to the assigned position between maximum advancing angle side and the maximum retardation angle side snaps in;

The second locking guiding groove, it extends and is provided with from march forward angular direction or retardation angle direction of said second locking hole, and under the state that the front end of said second locking component is snapped into, said vane rotor can rotate with respect to said rotary driving body relatively,

And said second locking component forms, and the compression area of advance and retreat direction both end sides is set at identical, and the same hydraulic pressure of the arbitrary hydraulic chamber in said advancing angle hydraulic chamber of said advance and retreat direction both end sides effect and retardation angle hydraulic chamber,

And, being provided with compression zone in the side of said second locking component, working hydraulic pressure is supplied with or is discharged to an end face side of this compression zone selectively, and the other end side is opened to barometric pressure via said vane rotor inside.

(invention i) is characterized in that, in the Ventilsteuerzeitsteuervorrichtung of the invention internal-combustion engine that h put down in writing,

Said first locking component and first locking hole constitute, and in the predetermined angular scope, said vane rotor rotates with respect to said rotary driving body said first locking component relatively in the state delimit that is sticked in first locking hole,

Said first locking component is sticked in first locking hole, and after second locking component was sticked in second locking hole, vane rotor just suffered restraints with respect to the relative rotation of said rotary driving body.

(invention j) is characterized in that, in the Ventilsteuerzeitsteuervorrichtung of the invention internal-combustion engine that i put down in writing,

In the bottom surface of the said second locking guiding groove, be provided with step-like step towards said second locking hole.

(invention k) is characterized in that, in the Ventilsteuerzeitsteuervorrichtung of the invention internal-combustion engine that j put down in writing,

Bottom surface at the said first locking guiding groove; Be provided with step-like step towards said first locking hole; Said first locking component withdraws from the step of the first locking guiding groove and after being sticked in said first locking hole, said second locking component withdraws from the step of the second locking guiding groove and is sticked in said second locking hole.

According to this invention; After first locking component is sticked in first locking hole through the first locking guiding groove; Second locking component is sticked in second locking hole through the second locking guiding groove; Thus, compare with the situation of two the said locking guiding grooves that extend singlely, the length of each locking guiding groove reduces.Thus, can reduce to close the breadth of circumferencial direction of each blade of this locking guiding groove.

(invention l) is characterized in that, in the Ventilsteuerzeitsteuervorrichtung of the invention internal-combustion engine that k put down in writing,

The step of being located at the said first locking guiding groove is more than the step of being located at the said second locking guiding groove.

(invention m) is characterized in that, invent in the Ventilsteuerzeitsteuervorrichtung of the internal-combustion engine of being put down in writing in first aspect,

The step surface of bottom surface of being located at the hypomere of the said second locking guiding groove is higher than the bottom surface step surface of the hypomere that is located at the first locking guiding groove.

The step of the hypomere through increasing the second locking guiding groove; Improve the intensity of the said stepped part that constitutes second locking hole; Therefore, though be sticked in second locking hole second locking component outer side surface repeatedly with stepped part (step surface) butt, also can seek to improve its durability.Need to prove, when the first lock part material is sticked in first locking hole,, but be connected to the interior edge face of the first dark locking hole,, also can seek to improve durability so put from this because the first lock part material is not to be connected to step surface.

(invention n) is characterized in that, in the Ventilsteuerzeitsteuervorrichtung of the invention internal-combustion engine that i put down in writing,

Said first locking hole forms roughly silkworm shape of plane.

(invention o) is characterized in that, in the Ventilsteuerzeitsteuervorrichtung of the invention internal-combustion engine that n put down in writing,

The said first locking guiding groove also forms roughly silkworm shape of plane.

Through forming such silkworm shape, obtain the level and smooth turning effort of first locking component of rotation along with the blade rotation.

(invention p) is characterized in that, in the Ventilsteuerzeitsteuervorrichtung of the invention internal-combustion engine that i put down in writing,

Said second locking hole forms roughly silkworm shape of plane.

(invention q) is characterized in that, in the Ventilsteuerzeitsteuervorrichtung of the invention internal-combustion engine that p put down in writing,

The said second locking guiding groove also forms roughly silkworm shape of plane.

Through forming such silkworm shape, obtain the level and smooth turning effort of second locking component of rotation along with the blade rotation.

Claims

1. the Ventilsteuerzeitsteuervorrichtung of an internal-combustion engine is characterized in that, has:

The rotary driving body, rotating force is delivered to this rotary driving body from bent axle, has the working room in the inside of this rotary driving body;

Vane rotor; Be fixed on the camshaft; And be set in the predetermined angular scope, rotate freely relatively with respect to said rotary driving body, this vane rotor has the blade that the working room of said rotary driving body is separated into advancing angle hydraulic chamber and retardation angle hydraulic chamber;

Locking component is arranged at the inside of said blade, is provided with to axial free to advance or retreatly;

Locking hole, when said blade rotated to the assigned position between maximum advancing angle side and the maximum retardation angle side relatively, the front end of said locking component was fastened on this locking hole;

Force application part applies the power towards said locking hole direction to said locking component;

Said locking component forms, and the compression area of advance and retreat direction both end sides is set at identical, and the same hydraulic pressure of the arbitrary hydraulic chamber in said advancing angle hydraulic chamber of said both end sides effect and said retardation angle hydraulic chamber;

Side at said locking component is provided with compression zone, and working hydraulic pressure is supplied with or discharged to an end face side of this compression zone selectively, and the other end side is opened to barometric pressure via said vane rotor inside.

2. the Ventilsteuerzeitsteuervorrichtung of internal-combustion engine as claimed in claim 1 is characterized in that,

Said locking component is made up of the lock pin that the side in cylindrical body is provided with the toroidal lip part that constitutes said compression zone.

3. the Ventilsteuerzeitsteuervorrichtung of internal-combustion engine as claimed in claim 1 is characterized in that,

Said rotary driving body has:

Shell cylindraceous, an axial at least end forms opening, is provided with shoe plate highlightedly at inner peripheral surface;

Sealing plate seals the opening end of this shell, and is formed with opening portion in the periphery of said relatively blade near the position of radially inner side;

Inside in the axial end face side of said blade is formed with the intercommunicating pore that an end is communicated with said opening portion, through the other end side atmosphere opening of this intercommunicating pore with said compression zone.

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

5. the Ventilsteuerzeitsteuervorrichtung of an internal-combustion engine is characterized in that, has:

First locking component is located at the inside of said blade, is provided with to axial free to advance or retreatly;

First locking hole, when said blade rotated to the assigned position between maximum advancing angle side and the maximum retardation angle side relatively, the front end of said first locking component was fastened on this first locking hole;

Force application part applies the power towards the said first locking hole direction to said first locking component;

The first locking guiding groove extends and is provided with from march forward angular direction or retardation angle direction of said first locking hole, and under the state that the front end of said first locking component snaps in, said vane rotor can rotate with respect to said rotary driving body relatively;

Said first locking component forms, and the compression area of advance and retreat direction both end sides is set at identical, and the same hydraulic pressure of the arbitrary hydraulic chamber in said advancing angle hydraulic chamber of said advance and retreat direction both end sides effect and said retardation angle hydraulic chamber;

And, being provided with compression zone in the side of said first locking component, working hydraulic pressure is supplied with or is discharged to an end face side of this compression zone selectively, and the other end side is opened to barometric pressure via said vane rotor inside.

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

On said vane rotor, be provided with a plurality of said blades;

In the blade different, to axially be provided with second locking component free to advance or retreatly with the said blade that is provided with said first locking component;

And, have:

Second locking hole; The front end of said second locking component can engage with this second locking hole or break away from, and this second locking hole is arranged on the position that the front end of said second locking component when said blade rotates to the assigned position between maximum advancing angle side and the maximum retardation angle side snaps in;

The second locking guiding groove extends and is provided with from march forward angular direction or retardation angle direction of said second locking hole, and under the state that the front end of said second locking component snaps in, said vane rotor can rotate with respect to said rotary driving body relatively;

Said second locking component forms, and the compression area of advance and retreat direction both end sides is set at identical, and the same hydraulic pressure of the arbitrary hydraulic chamber in said advancing angle hydraulic chamber of said advance and retreat direction both end sides effect and said retardation angle hydraulic chamber;

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

Said first locking component and said first locking hole constitute, and are sticked under the state of said first locking hole at said first locking component, and said vane rotor is only limit in the predetermined angular scope and can be rotated relatively with respect to said rotary driving body;

Said first locking component is sticked in said first locking hole, and after second locking component was sticked in said second locking hole, said vane rotor just suffered restraints with respect to the relative rotation of said rotary driving body.

8. the Ventilsteuerzeitsteuervorrichtung of an internal-combustion engine is characterized in that, has:

Locking component is located at the inside of said blade, is provided with to axial free to advance or retreatly;

Lock part, when said blade rotated to the assigned position between maximum advancing angle side and the maximum retardation angle side relatively, the front end of said locking component was fastened on this lock part;

Force application part applies the power towards said lock part direction to said locking component;

Also be provided with the engaging release unit that makes said locking component engage selectively or break away from respect to said lock part.