CN101852110B

CN101852110B - Variable valve device of engine

Info

Publication number: CN101852110B
Application number: CN 201010136525
Authority: CN
Inventors: 山西辉英; 石川秀男; 藤原一夫; 千叶一彦; 中沟大和
Original assignee: Honda Motor Co Ltd
Current assignee: Honda Motor Co Ltd
Priority date: 2009-03-31
Filing date: 2010-03-12
Publication date: 2013-05-29
Anticipated expiration: 2030-03-12
Also published as: CN101852110A; BRPI1000812A2; JP5312152B2; BRPI1000812B1; ITTO20100156A1; CN102865117A; IT1398994B1; JP2010236481A; CN102865117B

Abstract

The invention provides a variable valve device of an engine. In the variable valve device, the actuating mechanism generates power to drive the variable valve mechanism to act through changing the motion characteristic of the engine valve. The actuating mechanism is installed on the engine main body. Thereby, it is unnecessary to configure a specific part for the actuating mechanism so as to reduce the number of parts. A variable valve mechanism (29A) is borne on a specific engine main body component part (13) on one of two engine main body component parts (13, 14) between which variable valve chambers are formed (28); furthermore, a projecting portion (13c) projecting outwards is integrally formed; the actuating mechanism (64) is borne on an actuating mechanism bearing portion (91) which is coplanarly connected to a combined face (90) of the engine main body component part (13) and other engine main body component part (12) and formed on the projecting portion (13c); and a rotary rod (67) transmitting output of the actuating mechanism to the variable valve mechanism (29A) can be rotatably borne on the specific engine main body component part (13).

Description

The variable driving valve device of motor

Technical field

The present invention relates to a kind of variable driving valve device of motor, moving valve chamber in being formed at engine body, take in the active valve mechanism that has camshaft and drive this engine valve in the mode of the acting characteristic that can change engine valve, actuator is installed in described engine body, and the mode that this actuator produces to change the acting characteristic of described engine valve makes the power of described active valve mechanism action.

Background technique

The known variable driving valve device that following motor is arranged in patent documentation 1, one that namely consists of mutually combining in a plurality of engine body component parts of engine body is on cylinder cap or the head-shield, other containing box is installed, the driving mechanism that is supported with actuator and is used for the output of actuator is passed to the active valve mechanism side at this containing box.

Patent documentation 1:(Japan) No. 4188259 communique of special permission

Yet, in above-mentioned patent documentation 1 disclosed variable driving valve device, other containing box that need to be different from engine body, number of components increases, and, be incorporated in the skew of the linking department of the interior active valve mechanism of the interior moving valve chamber of engine body and actuator, if do not carry out strict size management, then might cause this skew to increase.

Summary of the invention

The present invention In view of the foregoing makes, and its purpose is to provide a kind of variable driving valve device of motor, does not need the special-purpose member for configuration actuator, can reduce number of components.

To achieve these goals, the variable driving valve device of motor of the present invention, in the moving valve chamber in being formed at engine body, take in the active valve mechanism that has camshaft and drive this engine valve in the mode of the acting characteristic that can change engine valve (Japanese: Machine Seki man's cap used in ancient times), actuator is installed in described engine body, the mode that this actuator produces to change the acting characteristic of described engine valve makes the power of described active valve mechanism action, the First Characteristic of this variable driving valve device is, mutually combine and consist of in a plurality of engine body component parts of described engine body, on a side's of two engine body component parts that form each other described moving valve chamber specific engines body component parts, be supported with described active valve mechanism, and, form and compare the bellying that other engine body component parts of being combined with described specific engines body component parts bloat more laterally, linking to each other with junction plane that described specific engines body component parts is combined to described other engine body component parts coplanarly and be formed on actuator's support of described bellying, be supported with described actuator, the dwang that the output of this actuator is passed to described active valve mechanism can be supported on described specific engines body component parts rotationally.

In addition, the variable driving valve device of motor of the present invention is on the basis of the structure with First Characteristic, and its Second Characteristic is that described actuator is along the sidewall configuration of described other engine body component parts and by described actuator support part supports.

In addition, the variable driving valve device of motor of the present invention is on the basis of the structure with Second Characteristic, it the 3rd is characterised in that, sidewall at described other engine body component parts, be provided with a plurality of juts in the mode that bloats laterally, it is logical that a plurality of described juts are inserted the coupling component that at least a portion in a plurality of described engine body component parts is connect, and described actuator is disposed between two juts that adjoin each other in a plurality of described juts.

The variable driving valve device of motor of the present invention, in the moving valve chamber in being formed at engine body, take in the active valve mechanism that has camshaft and drive this engine valve in the mode of the acting characteristic that can change engine valve, actuator is installed in described engine body, the mode that this actuator produces to change the acting characteristic of described engine valve makes the power of described active valve mechanism action, the 4th of this variable driving valve device is characterised in that, the described active valve mechanism that changes the acting characteristic of engine valve according to the movement of bar is incorporated in moving valve chamber, described bar can insert in the described camshaft with an open-ended hollow with moving axially, described moving valve chamber is formed at and mutually combines and consist of between two engine body component parts in a plurality of engine body component parts of described engine body, on a side's who forms each other two engine body component parts that move valve chamber specific engines body component parts, be provided with the opening portion relative with an end of described camshaft in the mode that can insert or extract described camshaft, be installed in the mode of sealing this opening portion on the cover of described specific engines body component parts, in the mode of the described bar of direct driving described actuator be installed.

The variable driving valve device of motor of the present invention is on the basis of the structure with First Characteristic～the 4th feature, it the 5th is characterised in that, on the cylinder cap as described specific engines body component parts, be equipped with described engine valve in the mode that can carry out on-off action, described actuator disposes in the mode that described engine valve is clipped in each other with the spark plug that is installed on described cylinder cap.

In addition, the crankcase 11 of mode of execution, cylinder body 12 and cylinder cap 13 are corresponding to the engine body component parts, cylinder cap 13,109 is corresponding to specific engines body component parts of the present invention, the outlet valve 25 of mode of execution is corresponding to engine valve of the present invention, and the solenoid 64 of mode of execution is corresponding to actuator of the present invention.

In accordance with a first feature of the invention, on specific engines body component parts, form and compare the bellying that other engine body component parts bloat laterally, be formed on actuator's support of this bellying, be supported with actuator, therefore, do not need the other special-purpose member different from the engine body that is used for configuration actuator, can reduce number of components.In addition, on specific engines body component parts, except actuator, also be supported with active valve mechanism, and, rotatably support has the dwang that the output of actuator is passed to active valve mechanism, therefore, do not need strict size management can reduce the skew of the linking department of actuator and active valve mechanism, and, because the junction plane that actuator's support and specific engines body component parts are combined to other engine body component parts is coplanar, therefore, can make the easy processing of actuator's support.

In addition, according to Second Characteristic of the present invention, because therefore actuator, can effectively utilize the space of the sidepiece of engine body to dispose actuator along the sidewall configuration of other engine body component parts of being combined with specific engines body component parts.

According to the 3rd feature of the present invention; because actuator is disposed at the sidewall of being located at other engine body component parts and a plurality of juts of bloating laterally between two juts of adjacency; therefore, can utilize other engine body component parts protection actuators.

According to the 4th feature of the present invention, because on a side's who forms each other two engine body component parts that move valve chamber specific engines body component parts, be provided with the opening portion that can make camshaft that active valve mechanism has insert or extract, and, the cover of this opening portion of sealing releasably is installed, actuator directly drives the bar that active valve mechanism has, so that it is mobile vertically in camshaft, described actuator is installed on described cover, therefore, do not need the other special-purpose member different from the engine body that is used for configuration actuator, and owing to utilize actuator directly to drive the bar of active valve mechanism, therefore, do not need the driving mechanism between actuator and the active valve mechanism, can reduce number of components.

And, according to the 5th feature of the present invention, because actuator and spark plug dispose in the mode that engine valve is clipped in each other, therefore, can guarantee that the configuration space of actuator is to avoid producing interference with spark plug.

Description of drawings

Fig. 1 is the major component sectional arrangement drawing of embodiment 1 motor;

Fig. 2 is the 2-2 line sectional drawing of Fig. 1;

Fig. 3 be Fig. 23 to looking section's enlarged view;

Fig. 4 be Fig. 34 to view;

Fig. 5 is the 5-5 line sectional drawing of Fig. 3;

Fig. 6 is the figure that valve promotes characteristic that opens of expression suction valve and outlet valve;

Fig. 7 is the 7-7 line sectional drawing of Fig. 2;

Fig. 8 is the 8-8 line sectional drawing of Fig. 2;

Fig. 9 is the 9-9 line sectional drawing of Fig. 2;

Figure 10 is the 10-10 line amplification profile of Fig. 3 under the decompression closed condition;

Figure 11 is the exploded perspective view of the mechanism of decompressor;

Figure 12 is the sectional drawing corresponding with Figure 10 under the decompression open mode;

Figure 13 is embodiment 2 the sectional drawing corresponding to Fig. 3;

Figure 14 be Figure 13 14 to view;

Figure 15 is embodiment 3 the sectional drawing corresponding to Fig. 2.

Description of reference numerals

10,108 engine bodies

11 crankcases as the engine body component parts

12 cylinder bodies as the engine body component parts

The 12a lug boss

13,109 cylinder caps as specific engines body component parts

The 13c bellying

14,110 head-shields as the engine body component parts

23 spark plugs

25 outlet valves as engine valve

28 moving valve chambers

32 camshafts

29A, 29B active valve mechanism

64 solenoids as actuator

67 dwangs

90 junction planes

91 actuator's supports

111 opening portions

112 covers

Embodiment

Below, with reference to the description of drawings embodiments of the present invention.

(embodiment 1)

Below, with reference to Fig. 1～Figure 12 embodiments of the invention 1 are described.At first, in Fig. 1 and Fig. 2, the engine body 10 of this motor is for example to be equipped on two-wheeled motor, described engine body 10 will mutually combine as crankcase 11, cylinder body 12, cylinder cap 13 and the head-shield 14 of a plurality of engine body component parts and consist of, cylinder body 12 have make piston 15 sliding freely chimeric cylinder thorax 16 and with crankcase 11 combinations, between itself and described cylinder body 12, form the cylinder cap 13 and cylinder body 12 combinations of the firing chamber 17 that faces described piston 15 tops, from a side opposite with described cylinder body 12, head-shield 14 and described cylinder cap 13 combinations.

Be provided with towards the suction port 18 of one lateral opening with towards the relief opening 19 of the another side opening of cylinder cap 13 at described cylinder cap 13, the suction tude 21 that the inlet air pathway 20 of described suction port 18 is led in formation is connected with described cylinder cap 13, has set up Fuelinjection nozzle 22 in this suction tude 21.

In addition, be equipped with suction valve 24 and outlet valve 25 at described cylinder cap 13 in the mode that can carry out on-off action, wherein, connection between these suction valve 24 described suction ports 18 of switching and the described firing chamber 17/block, the connection between these outlet valve 25 described relief openings 19 of switching and the described firing chamber 17/block.Suction valve 24 and outlet valve 25 utilize valve spring 26,27 to be applied in active force towards the valve closing direction.And then, the spark plug 23 that makes front end face described firing chamber 17 is installed at described cylinder cap 13.

With reference to Fig. 3, described suction valve 24 and outlet valve 25 utilize the active valve mechanism 29A that is incorporated in moving valve chamber 28 to drive and open and close in the lump, and this moving valve chamber 28 is formed between described cylinder cap 13 and the described head-shield 14.This active valve mechanism 29A has: camshaft 32, and it is disposed between described suction valve 24 and the outlet valve 25, and is provided with intake cam 30 and exhaust cam 31; Sliding cam 33, it has the cam profile that is different from exhaust cam 31, and with removable and can not counterrotating mode be installed on the periphery of described camshaft 32 vertically; The mechanism of decompressor 34, it is installed on described camshaft 32 in the mode that described exhaust cam 31 is clipped between itself and the described sliding cam 33; Air inlet side and exhaust side

pitman arm shaft

36,37, it has the axis parallel with described camshaft 32 and is supported by cylinder cap 13; Air inlet side rocking arm 38, it is driven in described intake cam 30 and drives into air valve 24 and open and close and shake and be supported on freely air inlet side pitman arm shaft 36; Exhaust side rocking arm 39, its relief cam 35 that is driven in described exhaust cam 31, described sliding cam 33 or the described mechanism of decompressor 34 drive outlet valve 25 and open and close, and shake and be supported on freely exhaust side pitman arm shaft 37; Bar 59, it can insert in the described camshaft 32 with moving axially.Described active valve mechanism 29A is by cylinder cap 13 supportings.

Be provided with integratedly at described cylinder cap 13: have clutch shaft bearing hole 40 the first support 42, have the second support 43 with coaxial the second bearing hole 41 in clutch shaft bearing hole 40.Described camshaft 32 is rotatably supported in described cylinder cap 13 via first and second ball bearing 44,45, and described first and second ball bearing 44, the 45th is along the pair of bearings that axially disposes across the interval of this camshaft 32.One end of camshaft 32 and clip the first ball bearing 44 and rotatably mounted by the first support 42 between the interior week in clutch shaft bearing hole 40, the partial rotation of the close the other end of described camshaft 32 connects the second bearing hole 41 freely, between interior week of the second bearing hole 41 and camshaft 32 the second ball bearing 45 is installed.And, camshaft 32 is pressed into first and second ball bearing 44,45 inner ring, described intake cam 30 and described exhaust cam 31 constitute intake cam 30 are disposed at the first ball bearing 44 sides and exhaust cam 31 is disposed at the second ball bearing 45 sides, and are integrally formed in described camshaft 32 between first and second ball bearing 44,45.The described mechanism of decompressor 34 is disposed between described intake cam 30 and the described exhaust cam 31, and sliding cam 33 is installed in described camshaft 32 in the position that exhaust cam 31 is clipped between the relief cam 35 of itself and the described mechanism of decompressor 34.

Described camshaft 32 is passed rotating power from not shown crank via timing driving mechanism 47, this timing driving mechanism 47 is at driven sprocket 48 and be fixedly installed on driving sprocket wheel (not shown) the volume link shape cam chain 50 of described crank and consist of, this driven sprocket 48 be fixed in described camshaft 32 from outstanding end that the second ball bearing 45 is given prominence to.Cam chain 50 is incorporated in movably chain and moves in the path 51, and this chain moves path 51 and forms across cylinder body 12, cylinder cap 13 and head-shield 14.

Pay close attention to Fig. 1, described intake cam 30 and exhaust cam 31 have: the circular-arc basic circle 30a of section, the 31a centered by the axis of described camshaft 32, compare the high-order 30b of section, 31b that the 30a of basic circle section, 31a connect between the outstanding and circumferential two ends with the 30a of basic circle section, 31a laterally.Make the phase shifting of the high-order 30b of section, 31b and be integrally formed in described camshaft 32.

End at the air inlet side rocking arm 38 that can joltily be supported by described air inlet side pitman arm shaft 36, axle is supported with the roller 52 that rolls and contact with intake cam 30, in the other end of this air inlet side rocking arm 38, screw togather the tappet screw 53 with the valve rod end 24a butt of suction valve 24 with can regulating the advance and retreat position.

In Fig. 4, exhaust side rocking arm 39 has integratedly: by the rotatably mounted 39a of carrying cylinder section of described exhaust side pitman arm shaft 37, certainly the first wrist 39b of extending to outlet valve 25 sides of the 39a of this carrying cylinder section, the second wrist 39c of extending to camshaft 32 sides from the described carrying cylinder 39a of section.The described carrying cylinder 39a of section is disposed at each other and is arranged between a pair of pitman arm shaft support 13a, the 13b of described cylinder cap 13 across the compartment of terrain, is passed the described carrying cylinder 39a of section by the exhaust side pitman arm shaft 37 of these pitman arm shaft supports 13a, 13b supporting.

At the front end of the first wrist 39b, as screwing togather in the mode with the valve rod end 25a butt of outlet valve 25 with the tappet screw 54 of outlet valve 25 interlocks and the valve linking department that links, this tappet screw 54 can be regulated the advance and retreat position.

In addition, at the front end of the second wrist 39c, be provided with can with the cam abutting part 55 of described exhaust cam 31, described sliding cam 33 and described relief cam 35 butts.This cam abutting part 55 constitutes to have: roller 56, and it is made as and can supports with described exhaust cam 31 and described sliding cam 33 butts and by the front end axle of the second wrist 39c; Abutting part 39d (with reference to Fig. 1 and Fig. 3), its make the described mechanism of decompressor 34 relief cam 35 butts and with described roller 56 in abutting connection with and be arranged at integratedly the front end of the second wrist 39c.The end of at least camshaft 32 sides of this abutting part 39d, from the direction along the axis of camshaft 32, it is identical or to compare described periphery more side-prominent to described camshaft 32 to form periphery with described roller 56.

And, on the direction of the axis of described camshaft 32 and described exhaust side pitman arm shaft 37, the width W of described cam abutting part 55 is the distance to the end face of described air inlet side rocking arm 38 sides of abutting part 39d from the end face of a side opposite with described air inlet side rocking arm 38 of described roller 56, one end of this cam abutting part 55 is the end face 56a of a side opposite with described air inlet side rocking arm 38 of described roller 56, an end face 39aa who compares the 39a of carrying cylinder section is the end face of pitman arm shaft support 13a side, more is positioned at axial inboard.

Described sliding cam 33 is between operating position (position shown in the solid line of Fig. 3 and Fig. 4) and non-operating position (position shown in the dotted line of Fig. 3 and Fig. 4), can move along the axial direction of described camshaft 32 and can not relatively rotate around the axis of this camshaft 32, chimericly in the above described manner be installed on the periphery of camshaft 32 and be supported, wherein, this operating position be near described exhaust cam 31 and with the cam abutting part 55 of exhaust side rocking arm 39 in the position of roller 56 butts, this non-operating position is for leaving to avoid the position of roller 56 butts in the cam abutting part 55 with described exhaust side rocking arm 39 from described exhaust cam 31.

In Fig. 5, described sliding cam 33 is so that the part of the waste gas that discharge spontaneous combustion chamber 17 is got back to the mode of firing chamber 17 described outlet valve 25 to be opened the EGR cam that valve drives, the high-order 33b of section that has the circular-arc basic circle 33a of section centered by the axis of described camshaft 32 and give prominence to laterally from the 33a of basic circle section, the 33a of basic circle section of sliding cam 33 forms the little path of the 31a of basic circle section than exhaust cam 31.

In addition, the high-order 33b of section is outstanding a little from the described basic circle 33a of section with the phase place of closing valve latter stage corresponding to the high-order 30b of section in the intake cam 30, and the circumferential two ends of the high-order 33b of section link to each other with the described basic circle 33a of section in the mode of describing smooth curve.And, when sliding cam 33 moves to the operating position of roller 56 butts in the cam abutting part 55 with exhaust side rocking arm 39, exhaust side rocking arm 39 rotates to utilize the high-order 31b of section of exhaust cam 31 to make outlet valve 25 open valve events, afterwards, keep closing the valve state by the 31a of the basic circle section butt with exhaust cam 31, but the latter stage when suction valve 24 closes valve events, as shown in Figure 6, exhaust side rocking arm 39 rotates a little, with the high-order 33b of section that utilizes sliding cam 33 outlet valve 25 is opened a little.Thus, in compression stroke, can temporarily open outlet valve 25, utilize waste gas to make the combustive activation of mixed gas in firing chamber 17, thereby can seek the minimizing of NOx, the raising of motor output and the reduction of fuel consumption etc.

On the other hand, when sliding cam 33 moves to the non-operating position that the roller 56 in the cam abutting part 55 of avoiding with exhaust side rocking arm 39 contacts, exhaust side rocking arm 39 only utilizes exhaust cam 31 rotary actuations, and outlet valve 25 carries out on-off action with the running-active status corresponding to the cam profile of exhaust cam 31.Namely, according to the movement of sliding cam 33 along the axial direction of camshaft 32, can switch carry out corresponding to the on-off action situation of the outlet valve 25 of the cam profile of exhaust cam 31 with corresponding to the cam profile of exhaust cam 31 on-off action and originally close valve during can access the running-active status of the temporary transient outlet valve of opening the valve state 25.

And, non-operating position at sliding cam 33, shown in the dotted line of Fig. 4, between the end face 39aa of the end face 56a of the roller 56 in described cam abutting part 55 and the described carrying cylinder 39a of section, dispose the first end face 33c of described exhaust cam 31 sides of facing of described sliding cam 33, and, the second end face 33d of a side opposite with the first end face 33c compares the end face 39aa of the described carrying cylinder 39a of section and is disposed at the outside, operating position at sliding cam 33, shown in the solid line of Fig. 4, the second end face 33d of this sliding cam 33 compares the end face 39aa of the described carrying cylinder 33d of section and is disposed at the inboard.

And the moving range W1 of the first end face 33c of sliding cam 33 is set to the scope across the end face 56a of roller 56, and the moving range W2 of the second end face 33d of sliding cam 33 is set to the scope across the end face 39aa of the described carrying cylinder 39a of section.

And, as shown in Figure 4, pass tappet screw 54 to the straight line of the axial centre CP of the abutment P of the tappet screw 54 of the valve rod end butt of outlet valve 25 and the 39a of carrying cylinder section in the exhaust side rocking arm 39, by being positioned at the sliding cam 33 with the operating position of described roller 56 butts.Be positioned at and the sliding cam 33 of the operating position of roller 56 butts of cam abutting part 55 and tappet screw 54 abutting part to outlet valve 25 butts, the axial centre CP that is disposed at respect to the 39a of carrying cylinder section is point-symmetric position.

In addition, at least one party at the opposing side of sliding cam 33 and exhaust cam 31, be provided with the projection or the stepped part that stop sliding cam 33 to be close to exhaust cam 31, in this embodiment 1, as shown in Figure 3, be provided with a plurality of projection 31c... in that the end face of sliding cam 33 sides of exhaust cam 31 is outstanding integratedly.

Described camshaft 32 has coaxial center hole 57 and forms hollow, is provided with the center hole 48a corresponding with described center hole 57 at driven sprocket 48.In addition, at camshaft 32, in a side opposite with described driven sprocket 48, screw togather coaxially the bolt 58 of the described center hole of sealing 57 ends.In addition, bar 59 at one end section has the path axial region 59a relative with described bolt 58 coaxially, and this bar 59 inserts described center hole 57 coaxially in axially displaceable mode, and the other end of bar 59 is outstanding from described driven sprocket 48.

In addition, the part at configuration sliding cam 33 is provided with pilot hole 60 at described camshaft 32, and this pilot hole 60 will link between the outer circumferential face of the inner peripheral surface of described center hole 57 and described camshaft 32 and axially extending more longways along described camshaft 32.And, in this embodiment 1, as shown in Figure 5, have with a pair of

pilot hole

60,60 of the axis of the axis C quadrature of described center hole 57 and be located at camshaft 32, the described sliding cam 33 and the described bar 59 that are mounted in axially displaceable mode in the periphery of camshaft 32 are by connecting described pilot hole 60... and linking at the single connection pin 61 that is sliding along the direction of described axis C in pilot hole 60....

Thus, sliding cam 33 can not rotate relatively around the axis of camshaft 32, and between operating position and non-operating position, can move along the axial direction of described camshaft 32, be installed on the periphery of this camshaft 32 and be supported so that this mode is chimeric, wherein, this operating position be near exhaust cam 31 and with the cam abutting part 55 of exhaust side rocking arm 39 in the position of roller 56 butts, this non-operating position is the position of roller 56 butts in the cam abutting part 55 that leaves to avoid exhaust side rocking arm 39 from exhaust cam 31.

Between described bar 59 and described bolt 58, be provided with around the helical Returnning spring 62 of the path axial region 59a of described bar 59 with dwindling, bar 59 is applied in active force by described Returnning spring 62 to this side that makes described sliding cam 33 be in non-operating position.

Described bar 59 is driven vertically by bar driving mechanism 63, and is mobile between non-operating position and operating position with the described sliding cam 33 that is used in the acting characteristic that changes the outlet valve 25 among the described active valve mechanism 29A.This bar driving mechanism 63 has: solenoid 64, and it is installed on engine body 10 makes the power of active valve mechanism 29A action change the acting characteristic of outlet valve 25 as actuator with generation; Dwang 67, its output with this solenoid 64 is delivered to the bar 59 of active valve mechanism 29A.

Mutually combine and consist of the crankcase 11 of a plurality of engine body component parts of conduct of engine body 10, cylinder body 12, in cylinder cap 13 and the head-shield 14, on a side's of the cylinder cap 13 that forms each other moving valve chamber 28 and head-shield 14 specific engines body component parts, in this embodiment 1, be on the cylinder cap 13, be supported with described active valve mechanism 29A, and, form and compare the bellying 13c that the cylinder body 12 with cylinder cap 13 combinations bloats laterally, link to each other and be formed on actuator's support 91 of described bellying 13c to the junction plane 90 of described cylinder body 12 combinations with cylinder cap 13 coplanarly, be supported with described solenoid 64.And solenoid 64 is configured between itself and described spark plug 23 across the position of described outlet valve 25 and suction valve 24, is installed on described actuator support 91 by a plurality of bolt 68....

In the lump with reference to Fig. 7, described dwang 67 via fulcrum 66 rotatably supports in described cylinder cap 13, so that the front end of the output shaft 65 that one end and described solenoid 64 have is connected and the other end is connected with bar 59.On head-shield 14, be disposed at described dwang 67 another distolateral bellying 14a and form with the bellying 13c of cylinder cap 13 and link to each other.

The joint that connects to the output shaft 65 of described solenoid 64 at described dwang 67 or the joint that connects to described bar 59, be the joint that connects to bar 59 in this embodiment 1, be provided be used to regulating the controlling mechanism 92 of described bar 59 corresponding to the amount of movement of the action of solenoid 64.The output shaft 65 of described solenoid 64 and the direct butt in an end of described dwang 67.

With reference to Fig. 8, described controlling mechanism 92 constitutes to have in the lump: be fixed in the other end of described dwang 67 welded nut 93, screw togather and connect the tappet screw 94 of dwang 67, the retainer nut 95 who screws togather and engage with described welded nut 93 butts with this tappet screw 94 with this welded nut 93.Described tappet screw 94 and described bar 59 butts.And, by unclamping described retainer nut 95, can regulate the axial advance and retreat position of tappet screw 94, thus, be conditioned corresponding to the amount of movement of the described bar 59 of the action of solenoid 64.

In addition, described cylinder cap 13 and described head-shield 14 make liner 96 be clipped in described cylinder cap 13 to the junction plane 97 of described head-shield 14 combinations and described head-shield 14 between the junction plane 98 of described cylinder cap 13 combinations and combination, and described controlling mechanism 92 is compared the described junction plane 97 of described cylinder cap 13 and is disposed at described head-shield 14 sides.

In addition, consisting of regularly the driven sprocket 48 of the part of driving mechanism 47 is disposed at and is clipped between camshaft 32 and the cylinder cap 13 and first and second ball bearing 44 of installing, a side of 45, be the second ball bearing 45 at this, and between the described dwang 67, for example by pair of

bolts

99,99 are fixed in camshaft 32, but the joint tappet screw 94 that described dwang 67 connects to described bar 59 when described solenoid 64 is in non-action status is to the abutting part of bar 59 butts, shown in the dotted line of Fig. 3, in this side of leaving from described camshaft 32, be set between itself and described driven sprocket 48 position across the interval.

In the lump with reference to Fig. 9, described solenoid 64 is along the sidewall configuration of cylinder body 12 and by 91 supportings of described actuator support, on cylinder body 12, be provided with a plurality of jut 12a... in the mode that bloats laterally, the jut 12a that adjoins each other among these juts 12a..., dispose described solenoid 64 between the 12a, these a plurality of jut 12a form the through hole 101... that passes as a plurality of through bolt 100... of coupling component, and this through bolt 100 will consist of the crankcase 11 of engine body 10, cylinder body 12, crankcase 11 in cylinder cap 13 and the head-shield 14, cylinder body 12 and cylinder cap 13 connect.

According to aforesaid bar driving mechanism 63, when solenoid 64 moves to the sides that output shaft 65 is given prominence to, the elastic force of dwang 67 resistance Returnning springs 62 rotates along the clockwise direction of Fig. 2, bar 59 is revolted the elastic force of Returnning springs 62 and is pressed into, sliding cam 33 is to moving near exhaust cam 31 and with the operating position of roller 56 butts in the cam abutting part 55 of exhaust side rocking arm 39, be under the non-action status at solenoid 64, the elastic force that sliding cam 33 utilizes Returnning spring 62 moves to the non-operating position that the roller 56 in the cam abutting part 55 that leaves from exhaust cam 31 to avoid with exhaust side rocking arm 39 contacts.

In the lump with reference to Figure 10 and Figure 11, exhaust pressure when the mechanism of decompressor 34 reduces engine start and make its easy starting, therefore, be under the lower state of the rotating speed of camshaft 32 in engine speed, open a little outlet valve on the opportunity of closing outlet valve 25 originally, the relief cam 35 that this mechanism of decompressor 34 has decompression counterweight 72 and links with decompression counterweight 72, and be disposed between intake cam 30 and the exhaust cam 31, wherein, this decompression counterweight 72 is sold 71 rotatably supports in intake cam 30 and exhaust cam 31 via the decompression with axis parallel with camshaft 32; Under the low state of engine speed, from the 31a of basic circle section of exhaust cam 31 outstanding and with the camshaft 32 of the abutting part 39d butt of exhaust side rocking arm 39 along the direction rotation shown in the arrow 73 of Figure 10, utilize the effect of the centrifugal force that accompanies therewith and produce, when decompression counterweight 72 is rotated, make this relief cam 35 not with the abutting part 39d butt of described exhaust side rocking arm 39.

Decompression counterweight 72 forms circular-arc in the mode that covers the roughly semi-circumference of camshaft 32 from the side, and, be configured between intake cam 30 and the exhaust cam 31 so that the intake cam 30 of the part of surface thereof and camshaft 32 is slidingly connected.The high-order 31b of section in one end of this decompression counterweight 72 and the exhaust cam 31 of described camshaft 32 disposes accordingly.And, on the face that faces described exhaust cam 31 sides of an end of decompression counterweight 72, be provided with the circular housing recess 74 of opening wide towards exhaust cam 31 sides, an end of chimeric cylindric support projection 75 in this housing recess 74.In addition, the other end in support projection 75, link to each other with the other end of support projection 75 coplanarly and be provided with integratedly the 75a of blade of a sword section that stretches out to the radial direction outside, the high-order 31b of the section butt in the exhaust cam 31 of the other end of support projection 75 and described camshaft 32.

Described decompression pin 71 passes this intake cam 30 from intake cam 30 sides, decompression counterweight 72, described support projection 75 and described exhaust cam 31, be provided with the first through hole 76 that described decompression pin 71 is passed at intake cam 30, end in described decompression counterweight 72, to be provided with the second through hole 77 that described decompression pin 71 is passed with the described housing recess 74 coaxial modes that link to each other, the high-order 31b of section in described exhaust cam 31, with described first and second through hole 76,77 coaxial and towards the mode that described intake cam 30 sides are opened wide be provided with make that described decompression pin 71 passes end inserting hole 78 arranged.

And, decompression pin 71 is inserted through the inserting hole 78 of the second through hole 77, support projection 75 and the exhaust outstanding 31 of the first through hole 76 of this intake cam 30, the counterweight 72 that reduces pressure from intake cam 30 sides, thus, one end of decompression counterweight 72 is via by intake cam 30 and the exhaust cam 31 decompression pin 71 from two-side supporting, and rotatably support is in intake cam 30 and exhaust cam 31.

And, the other end butt of described decompression pin 71 of the peripheral part of packing ring 79 (with reference to Fig. 3) and the dead end butt that makes an end and described inserting hole 78, thus, stop decompression pin 71 to break away from from described the first through hole 76, the second through hole 77, support projection 75 and inserting hole 78.Namely the interior perimembranous of this packing ring 79 is held between the inner ring that is used for the first ball bearing 44 that the maintenance of the interval between described the first ball bearing 44 and the intake cam 30 is certain and camshaft 32, the peripheral part of this packing ring 79 and intake cam 30 butts, and at the other end butt of described decompression pin 71 periphery of packing ring 79 is arranged, thereby can not need the special-purpose member for the axial position of determining decompression pin 71.

In addition, center on an end of the helical torsion spring 80 of described support projection 75, engage with the end card complex hole 81 that has of being located at described camshaft 32, the other end of torsion spring 80 engages with the card complex hole 82 of an end of being located at described decompression counterweight 72.Utilize the elastic force of this torsion spring 80, decompression counterweight 72 is applied in active force to this side of close camshaft 32 outer circumferential faces of the intermediate portion that makes this decompression counterweight 72.

Described relief cam 35 is disposed between another distolateral and described exhaust cam 31 of described decompression counterweight 72 in the position corresponding to the 31a of basic circle section of exhaust cam 31, and rotatably mounted by the Rellef cam shaft 84 that is embedded at described exhaust cam 31.And Rellef cam shaft 84 has the axis parallel with the axis of camshaft 32, and relief cam 35 is supported by camshaft 32 rotationally around the axis parallel with the axis of camshaft 32.

Described relief cam 35 is substantially shaped as and coaxial cylindric of described Rellef cam shaft 84, but the part of described exhaust cam 31 sides of this relief cam 35 is cut into otch in the mode that forms the planar surface portion 85 parallel with the axis of relief cam 35.That is, the periphery of exhaust cam 31 sides of relief cam 35 forms by the described planar surface portion 85 that links between the circular arc part 86 centered by the axis of Rellef cam shaft 84 and the circumferential two ends with this circular arc part 86 and consists of.This relief cam 35 can rotate between decompression closed condition and decompression open mode, this decompression closed condition as shown in figure 10, make the described planar surface portion 85 of the basic circle section 31a inboard that is positioned at described exhaust cam 31 face the outside, this decompression open mode makes the part of described circular arc part 86 outstanding towards the outside of the 31a of basic circle section of described exhaust cam 31 as shown in figure 12.

And, in the circular arc part 86 of relief cam 35 when the described basic circle 31a of section is side-prominent outwardly, the abutting part 39b of exhaust side rocking arm 39 and circular arc part 86 butts, thus, exhaust side rocking arm 39 rotates so that outlet valve 25 is opened a little.

The other end in described decompression counterweight 72, be pressed into the connection pin 87 with axis parallel with camshaft 32, make this connection pin 87 from the outstanding chimeric guiding groove 88 of protuberance of the counterweight 72 of reducing pressure, be arranged at the part of decompression counterweight 72 sides of this relief cam 35 along the radial direction of relief cam 35 with extending.And, because of the rotating speed of camshaft 32 larger, the centrifugal force that acts on decompression counterweight 72 is large, rotate at the active force of the described torsion spring 80 of decompression counterweight 72 resistance so that the intermediate portion of this decompression counterweight 72 under the decompression closed condition that the periphery of camshaft 32 is left, as shown in figure 10, the connection pin 87 chimeric with guiding groove 88 rotates in the lump with decompression counterweight 72, under this state, relief cam 35 is positioned at the pivotal position that makes its planar surface portion 85 in the inboard of the 31a of basic circle section of described exhaust cam 31 and face the outside, the abutting part 39b of exhaust side rocking arm 39 not with relief cam 35 butts, exhaust side rocking arm 39 shakes according to the cam profile of exhaust cam 31, and outlet valve 25 also carries out on-off action on the opportunity of the cam profile of following exhaust cam 31.In addition, because the rotating speed of camshaft 32 is less, pretend for the centrifugal force of decompression counterweight 72 little, utilize the active force of described torsion spring 80 to rotate so that under the close decompression open mode of camshaft 32 peripheries of the intermediate portion of this decompression counterweight 72 in decompression counterweight 72, as shown in figure 12, the connection pin 87 chimeric with guiding groove 88 rotates in the lump with relief cam 35, under this state, relief cam 35 is positioned at the part that makes its circular arc part 86 from the 31a of basic circle section of described exhaust cam 31 outstanding pivotal position laterally, circular arc part 86 butts of the abutting part 39b of exhaust side rocking arm 39 and relief cam 35, therefore, exhaust side rocking arm 39 shook according to described relief cam 35 a little on roller 56 and the opportunity that the 31a of basic circle section of exhaust cam 31 contacts, outlet valve 25 is irrelevant with the cam profile of exhaust cam 31, also opens a little valve opportunity closing valve.

And when decompression was opened, be set in the phase place that is offset a little from this opportunity the opportunity that outlet valve 25 is opened as shown in Figure 6 near the opportunity that outlet valve 25 is opened by sliding cam 33.

Then, this embodiment's 1 effect described.Camshaft 32 at active valve mechanism 29A, sliding cam 33 is not being supported relative to the mode of rotating and can move vertically, exhaust side pitman arm shaft 37 has the axis parallel with described camshaft 32 and is supported on cylinder cap 13, at the exhaust side rocking arm 39 that has by the rotatably mounted 39a of carrying cylinder section of described exhaust side pitman arm shaft 37, be provided with can with the cam abutting part 55 of sliding cam 33 butts and with outlet valve 25 interlocks and the tappet screw 54 that links.And being provided with cam abutting part 55 so that an end of cam abutting part 55 is the end face 56a of a side opposite with described air inlet side rocking arm 38 of described roller 56 at exhaust side rocking arm 39, an end face 39aa who compares the 39a of carrying cylinder section is the end face of pitman arm shaft support 13a side and be disposed at axial inboard.When sliding cam 33 is positioned at when avoiding non-operating position with described cam abutting part 55 butts to a side shifting of leaving from exhaust cam 31, between the end face 39aa of the end face 56a of cam abutting part 55 and the 39a of carrying cylinder section, dispose the first end face 33c that faces exhaust cam 31 sides of sliding cam 33, and, the second end face 33d of a side opposite with the first end face 33c compares the end face 39aa of the described carrying cylinder 39a of section and more is disposed at the outside, be positioned to exhaust cam 31 side shiftings and during with the operating position of described cam abutting part 55 butts, the second end face 33d of this sliding cam 33 compares the end 39aa of the described carrying cylinder 39a of section and is disposed at the inboard at sliding cam 33.

Therefore, can reduce the axial internal clearance of sliding cam 33, thus the time that the switching in the time of can shortening the acting characteristic that changes outlet valve 25 spends.And, constitute and utilize an exhaust side rocking arm 39 to obtain the acting characteristic of two outlet valves that differ from one another 25, thus, the axial width of exhaust side rocking arm 39 becomes larger, become larger along camshaft 32 axial intervals between tappet screw 54 and the cam abutting part 55, because of above-mentioned situation, when the outlet valve 25 that is caused by sliding cam 33 is opened the valve lifting, the load of toppling direction is in exhaust side rocking arm 39, it is excessive that the load of cam abutting part 55 might become, but when using sliding cam 33, by will being disposed at as the second end face 33d of sliding cam 33 exterior edge faces the inboard of the end face 39aa of the 39a of carrying cylinder section, thereby can prevent toppling over of exhaust side rocking arm 39.

In addition, at least one party at the opposing side of sliding cam 33 and exhaust cam 31, be provided with the projection or the stepped part that stop sliding cam 33 to be close to exhaust cam 31, in this embodiment 1, be provided with a plurality of projection 31c... in that the end face of sliding cam 33 sides of exhaust cam 31 is outstanding integratedly, therefore, sliding cam 33 to exhaust cam 31 sides near mobile state under, even if between sliding cam 33 and exhaust cam 31, there is the oil of lubricated usefulness, also can the anti-skidding cam 33 be close to exhaust cam 31, can guarantee that sliding cam 33 is from moving the smoothly action that the position moves to non-operating position.

In addition, shown in the dotted line of Fig. 3, also can constitute the decompression pin 71 perforation exhaust cams 31 as the part of the mechanism of decompressor 34, this decompression pin 71 is constituted the projection that stops sliding cam 33 to be close to exhaust cam 31 from exhaust cam 31 outstanding protuberances, if consist of as mentioned above, then can utilize simple structure to come being close to of anti-skidding cam 33 and exhaust cam 31.

In addition, be positioned at and the sliding cam 33 of the operating position of roller 56 butts of cam abutting part 55 and tappet screw 54 abutting part to outlet valve 25 butts, the axial centre CP that is disposed at respect to the 39a of carrying cylinder section is point-symmetric position, therefore, sliding cam 33 is at operating position and roller 56 butts, thus, with the rightabout counter-force from outlet valve 25 of the load of the toppling direction that acts on exhaust side rocking arm 25 from sliding cam 33, act on exhaust side rocking arm 39, thereby can suppress toppling over of exhaust side rocking arm 39.

In addition, be on the cylinder cap 13 at the cylinder cap 13 that forms each other moving valve chamber 28 and a side of head-shield 14, be supported with active valve mechanism 29A, and, form and compare the bellying 13c that cylinder body 12 bloats laterally, at actuator's support 91 upper supports that are formed at bellying 13c solenoid 64 is arranged, the dwang 67 that the output of this solenoid 64 is transmitted to active valve mechanism 29A, rotatably support is in cylinder cap 13, therefore, do not need the other special-purpose member different from engine body 10 for configuration solenoid 64, thereby can reduce number of components.In addition, on cylinder cap 13, except solenoid 64, also be supported with active valve mechanism 29A, and, dwang 67 rotatably supports that the output of this solenoid 64 is transmitted to active valve mechanism 29A are in cylinder cap 13, therefore, active valve mechanism 29A, solenoid 64 and dwang 67 are assembled in cylinder cap 13, can increase processing cost, do not need strict size to manage the skew of the linking department that can reduce solenoid 64 and active valve mechanism 29A, can improve the dimensional accuracy of the each several part to bar 59 from solenoid 64.And, because actuator's support 91 is coplanar to the junction plane 90 of cylinder body 12 combinations with cylinder cap 13, therefore, can make the easy processing of actuator's support 91.

In addition, because therefore solenoid 64, can effectively utilize the space of engine body 10 sidepieces to dispose solenoid 64 along the sidewall configuration of cylinder body 12 and by 91 supportings of described actuator support.

In addition; sidewall at cylinder body 12; the a plurality of jut 12a... that insert logical through bolt 100... arrange in the mode that bloats laterally; this through bolt 100... connects crankcase 11, cylinder body 12 and cylinder cap 13; solenoid 64 is configured between two jut 12a, the 12a that adjoin each other among a plurality of described jut 12a...; therefore, can utilize cylinder body 12 protection solenoids 64.

And, solenoid 64 is by 91 supportings of actuator's support, so that it is disposed between itself and described spark plug 23 across the position of described outlet valve 25 and suction valve 24, therefore, the configuration space that can guarantee solenoid 64 is to avoid and spark plug 23 produces and interferes.

The linearly operating of the bar 59 that described active valve mechanism 29A can have according to this active valve mechanism 29A changes the acting characteristic of outlet valve 25, and driving outlet valve 25 opens and closes, the output of solenoid 64 is passed to described bar 59 via dwang 64, the joint that connects to described solenoid 64 at described dwang 67 or the joint that connects to described bar 59, be provided with and regulate described bar 59 corresponding to the controlling mechanism 92 of the amount of movement of the action of solenoid 64, in this embodiment 1, be provided with controlling mechanism 92 at dwang 67 to the joint that described bar 59 connects, therefore, even if do not improve from solenoid 64 via the dimensional accuracy of dwang 67 to the each several part of bar 59, also can adjustable lever 59 corresponding to the amount of movement of the action of solenoid 64, can seek to reduce cost.

In addition, compare cylinder cap 13 to the junction plane 97 of head-shield 14 combinations, controlling mechanism 92 is disposed at head-shield 14 sides, therefore, can easily carry out the adjusting operation of controlling mechanism 92 under the state of pulling down head-shield 14 from cylinder cap 13, thereby can improve the adjustment operating efficiency.

In addition, described camshaft 32 is via first and second ball bearing 44 that disposes across the interval on it is axial, 45 rotatably supports are in described cylinder cap 13, be hung on driven sprocket 48 for cam chain 50 volumes that rotating power are passed to described camshaft 32, this driven sprocket 48 is disposed between the second ball bearing 45 and the described dwang 67 and is fixed in described camshaft 32, the joint that described dwang 67 connects to described bar 59 when described solenoid 64 is in non-action status, in this side of leaving from described camshaft 32, be set between itself and described driven sprocket 48 position across the interval, therefore, described driven sprocket 48 can and can easily not carry out by the second ball bearing 45 and dwang 67 obstruction to the assembling operation of described camshaft 32 assemblings.

And, bolt 58 is fixed in the end of described camshaft 32 in a side opposite with a side that disposes described dwang 67, between this bolt 58 and described bar 59, the Returnning spring 62 that this bar 59 is applied active force to described dwang 67 sides is installed, therefore, can after assembling dwang 67 or driven sprocket 48, carry out bar 59 is applied the assembling of the Returnning spring 62 of active force, thereby can improve packaging efficiency.

(embodiment 2)

With reference to Figure 13 and Figure 14 embodiments of the invention 2 are described.Part for corresponding with embodiment 1 only marks same reference character and illustrates, and omits detailed explanation.

This active valve mechanism 29B has: camshaft 32, and it is disposed between described suction valve 24 and the outlet valve 25, and is provided with intake cam 30 and exhaust cam 31; Sliding cam 33, it has the cam profile that is different from exhaust cam 31, and with removable and can not counterrotating mode be installed on the periphery of described camshaft 32 vertically; The mechanism of decompressor 34, it is installed on described camshaft 32 in the mode that described exhaust cam 31 is clipped between itself and the described sliding cam 33; Air inlet side and exhaust side pitman arm shaft 36,37, it has the axis parallel with described camshaft 32 and is supported by cylinder cap 13; Air inlet side rocking arm 38, it is driven in described intake cam 30 and drives into air valve 24 and open and close and shake and be supported on freely air inlet side pitman arm shaft 36; Exhaust side rocking arm 103, its relief cam 35 that is driven in described exhaust cam 31, described sliding cam 33 or the described mechanism of decompressor 34 drive outlet valve 25 and open and close, and shake and be supported on freely exhaust side pitman arm shaft 37; Bar 59, it can insert in the described camshaft 32 with moving axially.Described active valve mechanism 29B is by cylinder cap 13 supportings.

Exhaust side rocking arm 103 has integratedly: by the rotatably mounted 103a of carrying cylinder section of described exhaust side pitman arm shaft 37, certainly the first wrist 103b of extending to outlet valve 25 sides of the 103a of this carrying cylinder section, the second wrist 103c of extending to camshaft 32 sides from the described carrying cylinder 103a of section.The described carrying cylinder 103a of section is disposed at each other and is arranged between a pair of pitman arm shaft support 13a, the 13b of described cylinder cap 13 across the compartment of terrain, is passed the described carrying cylinder 103a of section by the exhaust side pitman arm shaft 37 of these pitman arm shaft supports 13a, 13b supporting.

At the front end of the first wrist 103b, as screwing togather in the mode with the valve rod end 25a butt of outlet valve 25 with the tappet screw 54 of outlet valve 25 interlocks and the valve linking department that links, this tappet screw 54 can be regulated the advance and retreat position.

In addition, at the front end of the second wrist 103c, be provided with can with the cam abutting part 104 of described exhaust cam 31, described sliding cam 33 and described relief cam 35 butts.This cam abutting part 104 constitutes to have: roller 56, and it is made as and can supports with described exhaust cam 31 butts and by the front end axle of the second wrist 103c; Abutting part 103d, it is made as and can and be located at the front end of the second wrist 103c in a side of described roller 56 with described sliding cam 33 butts; Abutting part 103e, its front end of being located at the second wrist 103c is so that relief cam 35 butts of the described mechanism of decompressor 34 and described roller 56 is clipped between this abutting part 103e and the described abutting part 103d.The end of at least camshaft 32 sides of abutting

part

103d, 103e, from the direction along the axis of camshaft 32, it is identical or to compare described outer circumferential described camshaft 32 side-prominent to form periphery with described roller 56.

And on the direction of the axis of described camshaft 32 and described exhaust side pitman arm shaft 37, the end face 103aa that an end 104a of described cam abutting part 104 compares the 103a of carrying cylinder section is the end face of pitman arm shaft support 13a side, is positioned at axial inboard.

Described sliding cam 33 is between operating position (position shown in the solid line of Figure 13 and Figure 14) and non-operating position (position shown in the dotted line of Figure 13 and Figure 14), can move along the axial direction of described camshaft 32 and can not relatively rotate around the axis of this camshaft 32, chimericly in the above described manner be installed on the periphery of camshaft 32 and be supported, wherein, this operating position be near described exhaust cam 31 and with the cam abutting part 104 of exhaust side rocking arm 103 in the position of abutting part 103d butt, this non-operating position is for leaving to avoid the position of the abutting part 103d butt in the cam abutting part 104 with described exhaust side rocking arm 103 from described exhaust cam 31.

And, non-operating position at sliding cam 33, shown in the dotted line of Figure 14, between the end face 103aa of an end 104a of described cam abutting part 104 and the described carrying cylinder 103a of section, dispose the first end face 33c of described exhaust cam 31 sides of facing of described sliding cam 33, and, the second end face 33d of a side opposite with the first end face 33c compares the end face 103aa of the described carrying cylinder 103a of section and is disposed at the outside, operating position at sliding cam 33, shown in the solid line of Figure 14, the second end face 33d of this sliding cam 33 compares the end face 103aa of the described carrying cylinder 103a of section and is disposed at the inboard.

And, the moving range W1 of the first end face 33c of sliding cam 33 is set to the scope across an end 104a of cam abutting part 104, and the moving range W2 of the second end face 33d of sliding cam 33 is set to the scope across the end face 103aa of the described carrying cylinder 103a of section.

Pass tappet screw 54 to the straight line of the axial centre CP of the abutment P of the tappet screw 54 of the valve rod end butt of outlet valve 25 and the 103a of carrying cylinder section in the exhaust side rocking arm 103, by being positioned at the sliding cam 33 with the operating position of the abutting part 103d butt of described cam abutting part 104.Be positioned at and the sliding cam 33 of the operating position of the abutting part 103d butt of cam abutting part 104 and tappet screw 54 abutting part to outlet valve 25 butts, the axial centre CP that is disposed at respect to the 103a of carrying cylinder section is point-symmetric position.

According to this embodiment 2, also can access the effect identical with above-described embodiment 1.

(embodiment 3)

With reference to Figure 15 embodiments of the invention 3 are described.Part for corresponding with embodiment 1 and embodiment 2 only marks same reference character and illustrates, and omits detailed explanation.

The engine body 108 of this motor for example is equipped on two-wheeled.Described engine body 108 will as the crankcase 11 (with reference to embodiment 1) of a plurality of engine body component parts, cylinder body 12, cylinder cap 109 and head-shield 110 in conjunction with and consist of, cylinder body 12 have make piston 15 sliding freely chimeric cylinder thorax 16 and with crankcase 11 combinations, described cylinder cap 109 and cylinder body 12 in conjunction with its with described cylinder body 12 between form the firing chamber 17 that faces described piston 15 tops, oneself side and cylinder cap 109 combinations opposite with described cylinder body 12 of head-shield 110.

Be incorporated in the active valve mechanism 29A of the moving valve chamber 28 that between described cylinder cap 109 and described head-shield 110, forms, by cylinder cap 109 supportings.The opening portion 111 that one end of the hollow camshaft 32 that has with this active valve mechanism 29A is relative is located at described cylinder cap 109 in the mode that can insert or extract described camshaft 32.Be removably installed in the mode of sealing this opening portion 111 on the cover 112 of described cylinder cap 109, in the mode of the bar 59 of direct driving active valve mechanism 29A solenoid 64 be installed.That is, the output shaft 65 of solenoid 64 coaxially with described bar 59 butts.

And solenoid 64 is with at it and be installed on that the mode across outlet valve 25 and suction valve 24 is installed on described cover 112 between the spark plug 23 of cylinder cap 109.

According to this embodiment 3, do not need and be used for the different other special-purpose member of the engine body 108 of configuration solenoid 64, and utilize solenoid 64 direct driveshafts 59, therefore, do not need the driving mechanism between solenoid 64 and the active valve mechanism 29A, can reduce number of components.

More than, embodiments of the present invention have been described, but the present invention is not limited to above-mentioned mode of execution, within not breaking away from the scope of the present invention that claim puts down in writing, can carry out various design alterations.

For example, also can constitute at the bellying that is formed at cylinder cap 13 and be provided with cylinder cap 13 to the coplanar actuator's support of the junction plane of head-shield 14 combinations, also can constitute in addition at the bellying that is formed at head-shield 14 and be provided with head-shield 14 to the coplanar actuator's support of the junction plane of cylinder cap 13 combinations.

Claims

1. the variable driving valve device of a motor, in the moving valve chamber (28) in being formed at engine body (10), take in and have camshaft (32) and drive the active valve mechanism (29A of this engine valve (25) in the mode of the acting characteristic that can change engine valve (25), 29B), actuator (64) is installed in described engine body (10), the mode that this actuator (64) produces with the acting characteristic that changes described engine valve (25) makes described active valve mechanism (29A, 29B) the power of action, this variable driving valve device is characterised in that

Mutually combine and consist of a plurality of engine body component parts (11 of described engine body (10), 12,13,14) in, at two that form each other described moving valve chamber (28) described engine body component parts (13,14) on a side's the cylinder cap (13), be supported with described active valve mechanism (29A, 29B), and, form and compare the bellying (13c) that the cylinder body (12) with described cylinder cap (13) combination bloats more laterally, be formed with and the actuator's support (91) that links to each other with junction planes described cylinder body (12) (90) described cylinder cap (13) at described bellying (13c) coplanarly, at this actuator's support (91) upper support described actuator (64) is arranged, the output of this actuator (64) is passed to described active valve mechanism (29A, dwang 29B) (67) can be supported on described cylinder cap (13) rotationally.

2. the variable driving valve device of motor as claimed in claim 1 is characterized in that, described actuator (64) supports along the sidewall configuration of described cylinder body (12) and by described actuator support (91).

3. the variable driving valve device of motor as claimed in claim 2, it is characterized in that, sidewall in described cylinder body (12), be provided with a plurality of juts (12a) in the mode that bloats laterally, it is logical that a plurality of described juts (12a) are inserted the coupling component that at least a portion in a plurality of described engine body component parts (11～14) is connect, and described actuator (64) is disposed between two juts (12a) that adjoin each other in a plurality of described juts (12a).

4. such as the variable driving valve device of each described motor in the claim 1～3, it is characterized in that, on described cylinder cap (13,109), be equipped with described engine valve (25) in the mode that can carry out on-off action, described actuator (64) and the spark plug (23) that is installed on described cylinder cap (13,109) dispose in the mode that described engine valve (25) is clipped in each other.