CN2841989Y - Valve operating system for internal combustion engine - Google Patents
Valve operating system for internal combustion engine Download PDFInfo
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- CN2841989Y CN2841989Y CNU2005200033393U CN200520003339U CN2841989Y CN 2841989 Y CN2841989 Y CN 2841989Y CN U2005200033393 U CNU2005200033393 U CN U2005200033393U CN 200520003339 U CN200520003339 U CN 200520003339U CN 2841989 Y CN2841989 Y CN 2841989Y
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- centrifugal weight
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- Valve Device For Special Equipments (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Abstract
The utility model provides a valve operating system for internal combustion engine. The valve operating system for internal combustion engine is provided with a compressing cam component (47) arranged on a cam axle (26), and the compressing cam component (47) can move between the operating position (C) which can make an exhausting supporting rod (27e) work in the direction of opening the valve in the compressing process and the non-operative position (D) which looses the exhausting supporting rod; the valve operating system is provided with a cam component (48) of the waste gas back flow arranged on the cam axle, and the cam component (48) can move between the non-operative position (F) loosing the exhausting supporting rod and the operating position (G) which makes the exhausting supporting rod work in the direction of opening the valve in the admission stroke of the internal combustion engine; the valve operating system is provided with a common centrifugal mechanism (46) driven by the cam axle, and the common centrifugal mechanism (46) can make the compressing cam component work in the operating position (C) in the starting rotary area (a) and work in the non-operative position (D) after starting; the common centrifugal mechanism can make the cam component of the waste gas back flow work in the non-operative position (F) in the low speed operation area (b) and work in the operating position (G) in the high speed operation area (c).
Description
Technical field
The utility model relates to a kind of valve gear of internal-combustion engine, this valve gear has the camshaft with the bent axle interlock, and be driven in intake cam, the exhaust cam that on this camshaft, forms and the intake cam driven member that opens and closes intake valve, exhaust valve respectively, exhaust cam driven member respectively, particularly, relate to and utilize above-mentioned exhaust valve, when starting, can bring into play pressure-reducing function, and when running up, bring into play the valve gear of the internal-combustion engine of exhaust gas recirculation function.
Background technique
In the valve gear of internal-combustion engine, when internal-combustion engine runs up, in aspirating stroke, exhaust valve is opened a bit a little, make exhaust gas recirculation in the firing chamber, to suppress the excessive rising of exhaust gas temperature, suppress NO
XGeneration, such device discloses in patent documentation 1 (open in fact clear 55-137245 communique).
But described valve gear in the past is though can bring into play the exhaust gas recirculation function, but, but do not have pressure-reducing function, promptly when internal combustion engine start, for alleviating the load of start-up operation, exhaust valve is opened a bit a little, suitably reduce the pressure in the cylinder.
Summary of the invention
Therefore, the purpose of this utility model provides a kind of valve gear that can bring into play the internal-combustion engine of pressure-reducing function and exhaust gas recirculation function.
In order to achieve the above object, the valve gear of internal-combustion engine of the present utility model has following various parts: with the camshaft of bent axle interlock; Intake cam driven member and exhaust cam driven member, be driven in the intake cam and the exhaust cam that on this camshaft, form respectively, and difference switch intake valve and exhaust valve, it first is characterised in that, it also has following various parts: the relief cam parts are arranged on the above-mentioned camshaft, in the internal-combustion engine compression stroke, make the driven member of this exhaust cam open the working position of working on the exhaust valve direction, and unclamp between the inoperative position of above-mentioned exhaust cam driven member and move; The exhaust gas recirculation cam part, be arranged on the above-mentioned camshaft, and, and in the air-intake of combustion engine stroke, make the driven member of this exhaust cam open between the working position of working on the exhaust valve direction mobile in the inoperative position of the driven member that unclamps above-mentioned exhaust cam; Shared centrifugal mechanism, by above-mentioned camshaft actuated, make above-mentioned relief cam parts in the startup rotary area of internal-combustion engine, be on the working position, be in after the startup on idle position, and, above-mentioned exhaust gas recirculation cam part is on idle position in the internal-combustion engine low rotational speed region, in high rotational speed region, is on the working position.
In addition, above-mentioned intake cam driven member and exhaust cam driven member correspond respectively to inlet ram and exhaust tappet among the utility model embodiment described later.
In addition, the valve gear of internal-combustion engine of the present utility model also has following second feature on the basis of first feature, above-mentioned centrifugal mechanism is made of following parts: centrifugal weight,, on the support unit that is fixedly installed on the above-mentioned camshaft, and can swing with pivot suspension to radial direction; Returnning spring applies elastic force to this centrifugal weight to the inboard of radial direction; Common driver part, swing interlock with above-mentioned centrifugal weight, and respectively be arranged on above-mentioned relief cam parts and exhaust gas recirculation cam part on cam engage, drive above-mentioned relief cam parts, it is on the working position in the internal combustion engine start rotary area, is being on the inoperative position after the startup, and drive above-mentioned exhaust gas recirculation cam part, it is on idle position in the low rotational speed region of internal-combustion engine, in high rotational speed region, is on the working position.
In addition, above-mentioned support unit and driver part, corresponding with driven gear 32 and driving ring 45 among the aftermentioned embodiment of the present utility model respectively.
Also have, the utility model also has following the 3rd feature on the basis of second feature, promptly, above-mentioned Returnning spring is made of first Returnning spring and second Returnning spring, above-mentioned first Returnning spring applies elastic force to the radial direction inboard to above-mentioned centrifugal weight all the time, above-mentioned second Returnning spring, begins this centrifugal weight is applied rebounding force to the radial direction inboard at this centrifugal weight when the foreign side of radial direction has swung more than or equal to predetermined angular.
Also have, the utility model also has following the 4th feature on the basis of second feature, promptly, above-mentioned centrifugal weight is made of first centrifugal weight and second centrifugal weight, and above-mentioned first centrifugal weight produces the centrifugal force that resists mutually with the elastic force of above-mentioned Returnning spring all the time in the rotary course of above-mentioned camshaft; At above-mentioned first centrifugal weight before the outside of radial direction swings to predetermined angular, above-mentioned second centrifugal weight becomes as a whole with first centrifugal weight, and the centrifugal force that resists mutually of generation and the elastic force of above-mentioned Returnning spring, and when above-mentioned first centrifugal weight outside radial direction side oscillation during more than or equal to predetermined angular, just separate with first centrifugal weight, do not produce the centrifugal force that resists mutually with the elastic force of above-mentioned Returnning spring.
According to first feature of the present utility model, as long as relief cam parts, exhaust gas recirculation cam part and common centrifugal mechanism are set on the camshaft of valve gear, just can make valve gear have pressure-reducing function and exhaust gas recirculation function, thereby the cheap valve gear that has pressure-reducing function and exhaust gas recirculation function can be provided.
In addition, according to second feature of the present utility model, constitute the common centrifugal mechanism of relief cam parts and exhaust gas recirculation cam part with common centrifugal weight and common driver part, by this simple structure, can reduce the cost of valve gear with pressure-reducing function and exhaust gas recirculation function.
Also have, according to the 3rd feature of the present utility model, improve and the common centrifugal weight of swing by means of rotating speed along with internal-combustion engine, and first and second Returnning springs that this swing applied reaction force, just can make relief cam parts and exhaust gas recirculation cam part carry out work successively by common driving ring, and, by the operating time of selected second Returnning spring, just can freely set the working zone of exhaust gas recirculation cam part, and it is irrelevant with the working zone of relief cam parts, therefore, as long as on valve gear, increase simple structure, cheap valve gear just can be provided, and this valve gear has mutual noninterference, the pressure-reducing function of desirable characteristic and exhaust gas recirculation function.
And then, according to the 4th feature of the present utility model, improve and first and second centrifugal weights of swing by means of rotating speed along with internal-combustion engine, and the common Returnning spring that this swing is applied reaction force, can make relief cam parts and exhaust gas recirculation cam part carry out work successively by common driving ring, and, by the non-productive work time of selected second centrifugal weight, just can freely set the working zone of exhaust gas recirculation cam part, and it is irrelevant with the working zone of relief cam parts, therefore, as long as on valve gear, increase simple structure, cheap valve gear just can be provided, and this valve gear has mutual noninterference, the pressure-reducing function of desirable characteristic and exhaust gas recirculation function.
Description of drawings
Fig. 1 is the longitudinal section side view with internal-combustion engine of valve gear of the present utility model;
Fig. 2 is the sectional drawing along the 2-2 line among Fig. 1;
Fig. 3 is the sectional drawing along the 3-3 line among Fig. 1;
Fig. 4 is the sectional drawing along the 4-4 line among Fig. 3;
Fig. 5 is the sectional drawing along the 5-5 line among Fig. 3;
Fig. 6 is and the corresponding job description figure of Fig. 5;
Fig. 7 is the sectional drawing along the 7-7 line among Fig. 3;
Fig. 8 is and the corresponding job description figure of Fig. 7;
Fig. 9 is the schematic representation of the working zone of expression relief cam parts and exhaust gas recirculation cam part;
Figure 10 is the plotted curve that concerns between the switching time of the expression angle of swing of crankshaft and intake valve and exhaust valve;
Figure 11 is the longitudinal section side view of camshaft peripheral part of the utility model second embodiment's valve gear;
Figure 12 is the sectional drawing along the 12-12 line among Figure 11;
Figure 13 is the sectional drawing along the 13-13 line among Figure 12;
Figure 14 is the sectional drawing along the 14-14 line among Figure 11;
Figure 15 is and the corresponding job description figure of Figure 14;
Figure 16 is the sectional drawing along the 16-16 line among Figure 11;
Figure 17 is and the corresponding job description figure of Figure 16;
Figure 18 is the longitudinal section side view of camshaft peripheral part of the utility model the 3rd embodiment's valve gear;
Figure 19 is the sectional drawing along the 19-19 line among Figure 18;
Figure 20 is the sectional drawing along the 20-20 line among Figure 19;
Figure 21 is the sectional drawing along the 21-21 line among Figure 18;
Figure 22 is and the corresponding job description figure of Figure 21;
Figure 23 is the sectional drawing along the 23-23 line among Figure 18;
Figure 24 is and the corresponding job description figure of Figure 23.
The drawing reference numeral explanation
E: internal-combustion engine;
A: the startup rotary area of internal-combustion engine
C: the high rotational speed region of internal-combustion engine
C: the working position of relief cam parts
D: the inoperative position of relief cam parts
F: the inoperative position of exhaust gas recirculation cam part
G: the working position of exhaust gas recirculation cam part
6: bent axle
17i: intake valve
17e: exhaust valve
26: camshaft
26i: intake cam
26e: exhaust cam
27i: intake cam driven member (inlet ram)
27e: exhaust cam driven member (exhaust tappet)
32: supporting part (driven gear)
35: centrifugal weight
35
1: first centrifugal weight
35
2: second centrifugal weight
43,44,53: Returnning spring
45: driver part (driving ring)
46: centrifugal mechanism
47: the relief cam parts
48: the exhaust gas recirculation cam part
58: the concave cam of relief cam parts
59: the concave cam of exhaust gas recirculation cam part
Embodiment
Below, the preferred embodiment of the present utility model shown in illustrates mode of execution of the present utility model with reference to the accompanying drawings.
Fig. 1 is the longitudinal section side view with internal-combustion engine of the valve gear that relates to first embodiment of the present utility model; Fig. 2 is the sectional drawing along the 2-2 line among Fig. 1; Fig. 3 is the sectional drawing along the 3-3 line among Fig. 1; Fig. 4 is the sectional drawing along the 4-4 line among Fig. 3; Fig. 5 is the sectional drawing along the 5-5 line among Fig. 3; Fig. 6 is and the corresponding job description figure of Fig. 5; Fig. 7 is the sectional drawing along the 7-7 line among Fig. 3; Fig. 8 is and the corresponding job description figure of Fig. 7; Fig. 9 is the schematic representation of the working zone of expression relief cam parts and exhaust gas recirculation cam part; Figure 10 is the plotted curve of the relation between switching time of the expression angle of swing of crankshaft and intake valve and exhaust valve; Figure 11 is the longitudinal section side view of camshaft peripheral part of the related valve gear of the utility model second embodiment; Figure 12 is the sectional drawing along the 12-12 line among Figure 11; Figure 13 is the sectional drawing along the 13-13 line among Figure 12; Figure 14 is the sectional drawing along the 14-14 line among Figure 11; Figure 15 is and the corresponding job description figure of Figure 14; Figure 16 is the sectional drawing along the 16-16 line among Figure 11; Figure 17 is and the corresponding job description figure of Figure 16; Figure 18 is the longitudinal section side view of camshaft peripheral part of the related valve gear of the utility model the 3rd embodiment; Figure 19 is the sectional drawing along the 19-19 line among Figure 18; Figure 20 is the sectional drawing along the 20-20 line among Figure 19; Figure 21 is the sectional drawing along the 21-21 line among Figure 18; Figure 22 is and the corresponding job description figure of Figure 21; Figure 23 is the sectional drawing along the 23-23 line among Figure 18; Figure 24 is and the corresponding job description figure of Figure 23.
At first, first embodiment of the present utility model shown in explanatory drawing 1～Figure 10.
Among Fig. 1～Fig. 3, the body of the internal-combustion engine 1 of internal-combustion engine E is that cylinder block 3 that extends by crankcase 2, from a side direction oblique upper of this crankcase 2 and the cylinder head 4 that is bonded on these cylinder block 3 upper-end surfaces are constituted.Bent axle 6 is housed in the crankcase 2, and is bearing in by bearing 5,5 on the left and right twice sidewall of crankcase, and above-mentioned bent axle 6 is connected on the piston 7 by connecting rod 8, and piston 7 is inlaid among the cylinder barrel 3a of cylinder block 3.On bent axle 6 protrudes out a end in crankcase 2 outsides, fixing flywheel 10, on the outer side surface of this flywheel 10, fixedly installed ring-type cooled blade 11.Also have, on the core of flywheel 10, fixedly installed the startup tube axle 12 that outwards protrudes vertically from cooled blade 11.The known back springing type starting electrical machinery 13 that bent axle 6 is started that is connected with this startup tube axle 12 is installed on the crankcase 2 by support 14.Another end of bent axle 6 is a clutch end portion, protrudes out the outside at another sidewall of crankcase 2.
On cylinder head 4, formed the firing chamber 15 that links to each other with cylinder barrel 3a, and inner suction port 16i and the relief opening 16e that opens wide to firing chamber 15, and, intake valve 17i and the exhaust valve 17e of these two suction port 16i of switch and relief opening 16e also be provided with.The valve gear 20 that drives these two intake valve 17i and exhaust valve 17e switch is arranged between crankcase 2 and the cylinder head 4.To be described in more detail below about this valve gear 20.
In addition, on cylinder head 4, screwing togather spark plug 21, its electrode is towards the firing chamber 15, and Carburetor 22 and the muffler 23 that is connected with the outer end of suction port 16i and relief opening 16e respectively is installed.
In addition, the fuel tank 24 adjacent with Carburetor 22 and muffler 23 also has been installed on the top of crankcase 2.
Below, valve gear 20 is described.
In Fig. 1～Fig. 3, valve gear 20 has following various parts: camshaft 26 is bearing on the left and right sidewall of crankcase 2, and is driven by bent axle 6 by timing transmission device 25; Inlet ram 27i and exhaust tappet 27e are bearing on the cylinder block 3, can be along axially being free to slide, and flange 27ia, the 27ea of its underpart are connected on the intake cam 26i and exhaust cam 26e of camshaft 26, and can sliding contact; Inlet push rod 28i and exhaust push rod 28e, their underparts separately are connected on the upper end portion of above-mentioned inlet ram 27i and exhaust tappet 27e, and upper end portion separately then extends to the top of cylinder head 4 always; Intake rocker 29i and exhaust rocker arm 29e, be bearing on a pair of spherical support unit 33,33 that is fixedly set on the cylinder head 4, and can freely swing, when intake rocker 29i is arranged to make one end thereof to be connected on the head of intake valve 17i, its another end is connected on the upper end portion of inlet push rod 28i, when exhaust rocker arm 29e then is arranged to make one end thereof to be connected on the head of exhaust valve 17e, its another end is connected on the upper end portion of exhaust push rod 28e.
And, when intake cam 26i and exhaust cam 26e upwards push inlet ram 27i and exhaust tappet 27e respectively, intake rocker 29i and exhaust rocker arm 29e are just by means of the inlet push rod 28i and the exhaust push rod 28e that jointly move with it, swing towards the direction of opening of intake valve 17i and exhaust valve 17e respectively, and inlet-valve spring 30i and the exhaust valve spring 30e that they are exerted pressure to closing direction is installed respectively on intake valve 17i and exhaust valve 17e.Cover the cylinder head cover 18 of the valve gear 20 on the cylinder heads 4 such as intake rocker 29i and exhaust rocker arm 29e, engage with the upper-end surface of cylinder head 4.
Above-mentioned timing transmission device 25 is by being fixedly installed on the actuation gear 31 on the bent axle 6 and being fixedly installed on the camshaft 26 and being made of with the driven gear 32 that 1/2 reduction speed ratio drives actuation gear 31.As shown in Figure 3 and Figure 4, surround the end of centrifugal weight 35 of U font of half circumference of camshaft 26, be bearing on this driven gear 32 by pivot 36.The center of gravity 37 of centrifugal weight 35 is on this U oxbow part, this U oxbow part can be around swing around the pivot 36, its swing is interval at the retracted position A (referring to Fig. 4, Fig. 5) that is connected on the wheel hub 32a of driven gear 32, and the outer side surface of above-mentioned U oxbow part is connected between the expanded position B on the block 38 that protrudes on the side that is arranged on driven gear 32.On the intermediate portion and swing end of this centrifugal weight 35, be provided with the first and second movable joints 40,41.Anchor portion is connected on common fixedly connected 42 of driven gear 32 and movable end 43a, the 44a of first and second Returnning springs 43,44 that are made of draft helical spring, is connected on the first and second movable attachment portions 40,41.First Returnning spring 43 all the time with the regulation setting load Fs1 with centrifugal weight 35 layback in radial direction, and between the movable end 44a and the second movable attachment portion 41 of second Returnning spring 44, be provided with certain play S, centrifugal weight 35 from retracted position A before the outside of radial direction swings to predetermined angular, the swing of 44 pairs of centrifugal weights 35 of second Returnning spring does not produce resistance.In other words, after the outside of radial direction swung to predetermined angular, second Returnning spring, 44 ability and 43 collaborative works of first Returnning spring produced the reaction force with centrifugal weight 35 layback in radial direction to centrifugal weight 35 from retracted position A.
As shown in Figure 3, between above-mentioned centrifugal weight 35 and exhaust cam 26e, from centrifugal weight 35 sides, on camshaft 26 successively suit driving ring 45, relief cam parts 47 and exhaust gas recirculation cam part 48.Driving ring 45 is enclosed within on the outer peripheral surface of camshaft 26, can freely rotate, a pair of connecting plate 35a, the 35a that is formed on the centrifugal weight 35 is arranged to, both sides along the sense of rotation of driving ring 45 clip the connection bump 45c that protrudes from driving ring 45 outer peripheral surfaces, and, order about driving ring 45 and rotate along with the outer side oscillation of centrifugal weight 35 to radial direction.In addition, driving ring 45 has axial retaining groove 45a on the circumferential surface within it, by means of this retaining groove 45a, and remaining between driven gear 32 and the exhaust cam 26e camshaft 26 all the time along axially extended pin 45b.By relatively rotating of driving ring 45 and camshaft 26, this root pin 45b can rotate on the outer peripheral surface of camshaft 26.
In Fig. 5～Fig. 8, relief cam parts 47 and exhaust gas recirculation cam part 48 are entrenched on a pair of guide surface parallel to each other 55,55 that forms on the bi-side of camshaft 26, and can radially sliding along camshaft 26.Like this, relief cam parts 47 just can slide between its working position C (Fig. 5) and inoperative position D (Fig. 6) along guide surface 55,55.These two working position C and inoperative position D are connected on the outer peripheral surface of camshaft 26 definite by relief cam parts 47 and interior edge face 56a, 56b on guide surface 55,55 orthogonal directions.In addition, exhaust gas recirculation cam part 48 can slide between its inoperative position F (Fig. 7) and working position G (Fig. 8) along guide surface 55,55.These two working position G and inoperative position F are connected on the outer peripheral surface of camshaft 26 definite by exhaust gas recirculation parts 48 and interior edge face 57a, 57b on guide surface 55,55 orthogonal directions.
As shown in Figure 5 and Figure 6, the middle body at the interior edge face 56b of the convex cam 47a of relief cam parts 47 side has formed the concave cam 58 with above-mentioned pin 45b collaborative work.This concave cam 58 is formed by inclined-plane 58a and circular arc bottom surface 58b, when centrifugal weight 35 remains on the retracted position A by means of the elastic force of first Returnning spring 43, inclined-plane 58a is pushed by pin 45b and forces relief cam parts 47 to be on the C of working position, circular arc bottom surface 58b is then at centrifugal weight 35 (state shown in Figure 6) after retracted position A has rotated predetermined angle, make relief cam parts 47 avoid the interference of pin 45b, allow that it moves to inoperative position D.Relief cam parts 47 are owing to formed above-mentioned concave cam 58, the just opposite direction skew of mind-set and concave cam 58 from relief cam parts 47 of its center of gravity, when pin 45b arrives the position relative with circular arc bottom surface 58b, relief cam parts 47 are because of acting on the centrifugal force on the above-mentioned center of gravity, and move to the direction of inoperative position D.
On the other hand, the middle body at the interior edge face 57b of the convex cam 48a of exhaust gas recirculation cam part 48 side has formed the concave cam 59 with above-mentioned pin 45b collaborative work.This concave cam 59 is formed by circular arc bottom surface 59a and inclined-plane 59b.59a this following period of time before centrifugal weight 35 turns to predetermined angular from retracted position A in circular arc bottom surface makes exhaust gas recirculation cam part 48 avoid the interference of pin 45b, allows that it moves to inoperative position F.Inclined-plane 59b then at centrifugal weight 35 because centrifugal force and when the outside of radial direction turns to more than or equal to predetermined angle, pushed by pin 45b and force exhaust gas recirculation cam part 48 to get back on the G of working position.Owing to formed above-mentioned concave cam 59, the just opposite direction skew of mind-set and concave cam 59 from exhaust gas recirculation cam part 48 of the center of gravity of exhaust gas recirculation cam part 48, when pin 45b arrived the position relative with circular arc bottom surface 59a, exhaust gas recirculation cam part 48 just moved to the direction of working position G owing to acting on the centrifugal force on the above-mentioned center of gravity.
As mentioned above, by the collaborative work of centrifugal weight 35, first, second Returnning spring 43,44 and driving ring 45, constituted the centrifugal mechanism 46 that makes relief cam parts 47 and 48 work of exhaust gas recirculation cam part jointly.
Below, the effect of present embodiment is described.
When bent axle 6 rotated, camshaft 26 just was driven with 1/2 reduction speed ratio by timing transmission device 25 by bent axle 6.Then, in aspirating stroke, intake cam 26i upwards pushes inlet push rod 28i by inlet ram 27i, makes intake rocker 29i swing, thereby pushing intake valve 17i makes it overcome the elastic force of inlet-valve spring 30i and opens.In addition, in exhaust stroke, exhaust cam 26e upwards pushes inlet push rod 28e by exhaust tappet 27e, makes exhaust rocker arm 29e swing, thereby pushing exhaust valve 17e makes it overcome the elastic force of exhaust valve spring 30e and opens.Figure 10 represents the distribution of the switching time of this intake valve 17i and exhaust valve 17e.
In addition, in Fig. 9, be in when starting rotary area a at internal-combustion engine, promptly rotational speed N e from zero until when being lower than between the regulation rotational speed N e1 of idling speed, as shown in Figure 4 and Figure 5, centrifugal weight 35 remains on the retracted position A by means of the setting load Fs1 of first Returnning spring 43.At this moment, because connection bump 45c and connecting plate 35a, 35a by engaging mutually, and determined the pin 45b of the driving ring 45 of position, inclined-plane 58a by means of the concave cam 58 of 35 pairs of relief cam parts 47 of centrifugal weight exerts pressure, and makes on the working position C that convex cam 47a outwards protrudes from the basic circle of exhaust cam 26e so relief cam parts 47 just remain on.Therefore, if operation is used for the back springing type starting electrical machinery 13 of starting apparatus combustion engine E now, because when making bent axle 6 startings by starting tube axle 12 by starting electrical machinery 13, also driven camshaft 26 by timing transmission device 25, so, just as mentioned above, in the compression stroke of piston 7, convex cam 47a by means of relief cam parts 47 makes progress jack-up a bit a little with exhaust tappet 27e, just makes exhaust valve 17e open a bit a little by exhaust push rod 28e and exhaust rocker arm 29e.At this moment, the distribution of time as shown in figure 10.The result, a part of pressurized gas in the cylinder barrel 3a is just discharged from relief opening 16e, has so just suppressed the rising of compression pressure, thereby has alleviated the operation load of starting electrical machinery 13, effectively starting more trippingly of bent axle 6, thus the internal combustion function is started at an easy rate.
Behind the internal combustion engine start, when the rotational speed N e of internal-combustion engine surpasses the regional a that starts rotating speed, just as shown in Figure 6, the centrifugal weight 35 that is produced because of centrifugal force Fw is around the moment of torsion of pivot 36, just surpass centrifugal weight 35 that the setting load Fs1 by first Returnning spring 43 produced moment of torsion around pivot 36, make the outer side oscillation of centrifugal weight 35 from retracted position A towards radial direction, this swing is delivered to connection bump 45c from connecting plate 35a, make driving ring 45 to counterclockwise rotating, and pin 45b is moved towards the position relative with the bottom surface 58b of the concave cam 58 of relief cam parts 47.Therefore, relief cam parts 47 just are not subjected to the obstruction of pin 45b, move to inoperative position D under action of centrifugal force, and make its convex cam 47a retreat into the basic circle inside of exhaust cam 26e.
In this process, as shown in Figure 7, on exhaust gas recirculation cam part 48, because the bottom surface 59a of its concave cam 59 is relative with the pin 45b of driving ring 45, so exhaust gas recirculation cam part 48 just can not be subjected to the obstruction of pin 45b, remain on idle position F by means of centrifugal force, and make its convex cam 48a retreat into the basic circle inside of exhaust cam 26e.
As mentioned above, exhaust valve 17e only relies on the work of exhaust cam 26e to carry out switch control.And, when internal-combustion engine rotational speed Ne is in the low rotational speed region b of internal-combustion engine of Ne1～Ne2, still continue this state.Then, as shown in Figure 7, when the rotational speed N e of internal-combustion engine reaches Ne2, because the action of centrifugal weight 35, play S between the movable end 44a of the second movable attachment portion 41 of centrifugal weight 35 and second Returnning spring 44 disappears, and second Returnning spring 44 just begins centrifugal weight 35 is worked.Therefore, after this, made the moment of torsion of centrifugal weight 35 because of what the reposition force Fs2 of the reposition force Fs1 of first Returnning spring 43 and second Returnning spring 44 produced around pivot 36, with the centrifugal weight 35 that produces because of centrifugal force Fw around the mutual balance of the moment of torsion of pivot 36, thereby determined the position of centrifugal weight 35, afterwards, centrifugal weight 35 is with the rising of internal-combustion engine rotational speed Ne, and its swing speed just slows down.
Then, when the rotational speed N e of internal-combustion engine surpasses Ne2, when internal-combustion engine E enters high rotational speed region C, the centrifugal weight 35 final expanded position B that arrive on the block 38 that is connected on the driven gear 32, meanwhile, because driving ring 45 is further to counterclockwise rotating, pin 45b just is connected on the inclined-plane 59b of concave cam 59 of exhaust gas recirculation cam part 48, make exhaust gas recirculation cam part 48 overcome its centrifugal force, move on the G of working position, so exhaust gas recirculation cam part 48 just makes its convex cam 48a protrude from the basic circle of exhaust cam 26e.Therefore, as mentioned above, in the aspirating stroke of piston 7, with exhaust tappet 27e jack-up a little upwards, just can open exhaust valve 17e a bit a little by exhaust push rod 28e and exhaust rocker arm 29e by means of the convex cam 48a of exhaust gas recirculation cam part 48.As a result, the waste gas that remains in relief opening 16e place just can be inhaled in the firing chamber 15, has promptly carried out exhaust gas recirculation.When these waste gas carry out combustion of mixed gas in the expansion stroke in stage afterwards, can suppress the excessive rising of combustion temperature, in reducing waste gas, in the NOx concentration, can also reduce the concentration of HC, help improving its low fuel consumption performance.
As mentioned above, by means of the shared centrifugal weight of swinging along with the raising of internal-combustion engine rotational speed Ne 35, first and second Returnning spring 43 with this swing of opposing, 44, can make relief cam parts 47 and 48 work of exhaust gas recirculation cam part successively by shared driving ring 45, and, by the work period of selected second Returnning spring 44, promptly, play S on the movable end 44a of selected second Returnning spring 44, just can freely set the working zone of exhaust gas recirculation cam part 48, and it is irrelevant with the working zone of relief cam parts 47, therefore, as long as on valve gear 20, increase simple structure, the cheap valve gear of expense 20 just can be provided, this valve gear 20 has the pressure-reducing function and the exhaust gas recirculation function of the characteristic of desirable mutual noninterference.
Below, second embodiment of the present utility model shown in Figure 11～Figure 17 is described.
As Figure 11 and shown in Figure 12, be bearing in the centrifugal weight 35 of the centrifugal mechanism 46 on the driven gear 32 by pivot 36, the same U font that is with a last embodiment, its center of gravity 37 is on U oxbow part.Centrifugal weight 35 can be swung between retracted position A and expanded position B around pivot 36, wherein retracted position A is the position that the U oxbow of centrifugal weight 35 partly is connected to the wheel hub 32a of driven gear 32, and expanded position B is that the outer side surface of above-mentioned U oxbow part is connected to the position on the block 38 that protrudes on the side that is arranged on driven gear 32.The same with the foregoing description, be connected on the fixedly connected part 42 of driven gear 32 at the fixed end that is provided with movable attachment portion 40, the first Returnning springs 43 on this centrifugal weight 35, its movable end 43a then is connected on the movable attachment portion 40.This first Returnning spring 43 has the setting load Fs1 of regulation, always centrifugal weight 35 is pulled to the inboard of radial direction.
Different with the foregoing description, the spiral part 44b of second Returnning spring 44 that constitutes with torsion-coil spring is enclosed within on the excircle of above-mentioned pivot 36, under the state that the setting load Fs2 of the regulation on the torsional direction is applied on this spiral part 44b, the first and second arm 44c, the 44d of this second Returnning spring 44 just clip pivot 36, and fastening is on first and second baffle plates 62,63 that are formed on the centrifugal weight 35.The fore-end of the first arm 44c more stretches out than the end of centrifugal weight 35, in its side of fore-end, separates the interval L of regulation, protrudes to be provided with relative backing pin 61 on the side of driven gear 32.In addition, this second Returnning spring 44 centrifugal weight 35 from retracted position A before the outside of radial direction swings to predetermined angular, whole spring is with centrifugal weight 35 swings, and do not hinder the swing of centrifugal weight 35, but, when centrifugal weight 35 from retracted position A when the outside of radial direction swings to more than or equal to predetermined angular, owing to the first arm 44c is subjected to stopping of backing pin 61 spiral part 44b is further reversed, so, produce the reaction force that centrifugal weight 35 is pulled to the inboard of radial direction just with 43 collaborative works of first torsion spring.
Because other structure is all same as the previously described embodiments, so in Figure 11～Figure 17, the part that every and the foregoing description are corresponding is all marked identical label, and omits its explanation.
So, among the startup rotary area a of the rotational speed N e of internal-combustion engine this section internal-combustion engine before zero to the regulation rotational speed N e1 that is lower than idling speed (referring to Fig. 9), as Figure 12 and shown in Figure 14, centrifugal weight 35 remains on the retracted position A by means of the setting load Fs1 of first Returnning spring 43.Therefore, the same with the foregoing description, because the pin 45b of the driving ring 45 that connection bump 45c and connecting plate 35a, 35a by mutual engaging are positioned, inclined-plane 58a by the concave cam 58 of 35 pairs of relief cam parts 47 of centrifugal weight exerts pressure, and makes its convex cam 47a go up (referring to Figure 14) from the working position C that the basic circle of exhaust cam 26e outwards protrudes so relief cam parts 47 just remain on.At this moment, if operation is used for the back springing type starting electrical machinery 13 of starting apparatus combustion engine E, when making bent axle 6 startings by startup tube axle 12, also driven camshaft 26 by timing transmission device 25 with starting electrical machinery 13.In the compression stroke of piston 7, by means of the convex cam 47a of relief cam parts 47 with exhaust tappet 27e a little upwards jack-up a bit just make exhaust valve 17e open a bit a little by exhaust push rod 28e and exhaust rocker arm 29e.At this moment, the distribution of time is identical with the situation of the foregoing description, as shown in figure 10.As a result, a part of pressurized gas in the cylinder barrel 3a is just discharged from relief opening 16e, owing to suppressed the rising of compression pressure, has alleviated the operation load of starting electrical machinery 13, makes bent axle 6 effectively to start more trippingly, thereby the internal combustion function is started at an easy rate.
Behind the internal combustion engine start, when the rotational speed N e of internal-combustion engine surpasses when starting rotating speed regional, the centrifugal weight 35 that is produced because of centrifugal force Fw is around the moment of torsion of pivot 36, just surpass centrifugal weight 35 that the setting load Fs1 by first Returnning spring 43 produced moment of torsion around pivot 36, make the outer side oscillation of centrifugal weight 35 from retracted position A towards radial direction, this swing is delivered to connection bump 45c from connecting plate 35a, make driving ring 45 to counterclockwise rotating, and pin 45b is moved towards the position relative with the bottom surface 58b of the concave cam 58 of relief cam parts 47.Therefore, relief cam parts 47 just are not subjected to the obstruction of pin 45b, move to inoperative position D under action of centrifugal force, and make its convex cam 47a retreat into the basic circle inside of exhaust cam 26e.
In this process, as shown in figure 16, on exhaust gas recirculation cam part 48, because the bottom surface 59a of its concave cam 59 is relative with the pin 45b of driving ring 45, so exhaust gas recirculation cam part 48 just can not be subjected to the obstruction of pin 45b, remain on idle position F by means of centrifugal force, and make its convex cam 48a retreat into the basic circle inside of exhaust cam 26e.
As mentioned above, exhaust valve 17e only relies on the work of exhaust cam 26e to carry out switch control.And, when internal-combustion engine rotational speed Ne is in the low rotational speed region b of internal-combustion engine of Ne1～Ne2 (referring to Fig. 9), still continue this state.Then, as Figure 15, shown in Figure 16, when internal-combustion engine rotational speed Ne reaches Ne2, because the action of centrifugal weight 35, the first arm 44c of second Returnning spring 44 is blocked by the backing pin 61 of driven gear 32, makes spiral part 44b further reverse, so, its reaction force and 43 collaborative works of first Returnning spring pull to centrifugal weight 35 inboard of radial direction.Therefore, after this, because the centrifugal weight 35 that the reposition force Fs2 of the reposition force Fs1 of first Returnning spring 43 and second Returnning spring 44 is produced is around the moment of torsion of pivot 36, with the centrifugal weight 35 that produces because of centrifugal force Fw around the mutual balance of the moment of torsion of pivot 36, thereby determined the position of centrifugal weight 35, afterwards, with the rising of internal-combustion engine rotational speed Ne, the swing speed of centrifugal weight 35 just slows down.
Then, when the rotational speed N e of internal-combustion engine surpasses Ne2 (referring to Fig. 9), when internal-combustion engine E enters high rotational speed region C, the centrifugal weight 35 final expanded position B that arrive on the block 38 that is connected on the driven gear 32, meanwhile, because driving ring 45 is further to counterclockwise rotating, as shown in figure 17, pin 45b just is pressed on the inclined-plane 59b of concave cam 59 of exhaust gas recirculation cam part 48, make exhaust gas recirculation cam part 48 overcome its centrifugal force, move on the G of working position, so exhaust gas recirculation cam part 48 just makes its convex cam 48a protrude from the basic circle of exhaust cam 26e.Therefore, in the aspirating stroke of piston 7, by means of the convex cam 48a of exhaust gas recirculation cam part 48 with exhaust tappet 27e a little upwards jack-up a bit just can pass through exhaust push rod 28e and exhaust rocker arm 29e, 17e opens a bit a little exhaust valve.As a result, the waste gas that remains in relief opening 16e place just can be inhaled in the firing chamber 15, promptly carries out exhaust gas recirculation.When these waste gas carry out mixture combustion in the expansion stroke in stage afterwards, can suppress the excessive rising of combustion temperature, in reducing waste gas, in the NOx concentration, can also reduce the concentration of HC, help improving its low fuel consumption performance.
As mentioned above, in this second embodiment, also by means of the shared centrifugal weight of swinging along with the raising of internal-combustion engine rotational speed Ne 35, first and second Returnning springs 43 with this swing of resistance, 44, can make relief cam parts 47 and 48 work of exhaust gas recirculation cam part successively by shared driving ring 45, and, by the first arm 44c of selected second Returnning spring 44 and the butt time of backing pin 61, just can freely set the working zone of exhaust gas recirculation cam part 48, and it is irrelevant with the working zone of relief cam parts 47, therefore, as long as on valve gear 20, increase simple structure, the cheap valve gear of expense 20 just can be provided, and this valve gear 20 has the pressure-reducing function and the exhaust gas recirculation function of the desired characteristic of mutual noninterference.
Below, the 3rd embodiment of the present utility model shown in Figure 18～Figure 24 is described.
As Figure 18 and shown in Figure 19, the centrifugal weight of centrifugal mechanism 46 is by first centrifugal weight 35 that is bearing in by common pivot 36 on the driven gear 32
1With second centrifugal weight 35
2Constitute.First centrifugal weight 35
1Make the U font roughly the same with first embodiment's centrifugal weight 35, and its center of gravity 37
1On the curved section of U font.First centrifugal weight 35
1Around pivot 36, between retracted position A and expanded position B, can swing, wherein retracted position A is that the U oxbow partly is connected to the position on the wheel hub 32a of driven gear 32, and the expanded position B position that to be the outer side surface of above-mentioned U oxbow part be connected on the block 38 that protrudes on the side that is arranged at driven gear 32.The same with first embodiment's centrifugal weight 35, all the time this first centrifugal weight 35
1Pull to the movable end 53a of Returnning spring 53 of the inboard of radial direction with the setting load Fs of regulation, be connected this first centrifugal weight 35
1Movable joint 40 on, and a pair of connecting plate 35a, the 35a that clip the connection bump 45c of driving ring 45 are arranged on first centrifugal weight 35
1On.
Second centrifugal weight 35
2Bend to the shape of fishhook, surround half circumference, and part has and first centrifugal weight 35 therebetween above camshaft 26
1Center of gravity 37
1Approaching center of gravity 37
2This intermediate portion can be around pivot 36, the retracted position J (referring to Figure 19) on the outer peripheral surface of the wheel hub 32a that is connected to driven gear 32, and front end is connected between the expanded position K (referring to Figure 24) on the outer peripheral surface of same wheel hub 32a and waves.Second centrifugal weight 35
2Retracted position J and the angle of waving between the expanded position K be set than first centrifugal weight 35
1Retracted position A and expanded position B between to wave angle little.At this second centrifugal weight 35
2Be provided with abutting part 35
2a, second centrifugal weight 35
2When between above-mentioned retracted position J and expanded position K, waving, this abutting part 35
2aBe connected to first centrifugal weight 35
1Front end on (referring to Figure 19 and Figure 20).At first centrifugal weight 35
1On formed can with second centrifugal weight 35
2Or several projectioies 64 (referring to Figure 20) of side slide relative contact so that first and second centrifugal weights 35
1, 35
2Slide relative successfully.
Because other structure is all same as the previously described embodiments, so in Figure 18～Figure 24, every part corresponding to those in the first embodiment is marked with same label, and omits its explanation.
So, among the startup rotary area a of this section internal-combustion engine of the rotational speed N e of internal-combustion engine before zero to the regulation rotational speed N e1 that is lower than idling speed (referring to Fig. 9), as Figure 19 and shown in Figure 21, first centrifugal weight 35
1Remain on the retracted position A by means of the setting load Fs of Returnning spring 53.Therefore, the same with first embodiment's situation, because the pin 45b of the driving ring 45 that connection bump 45c and connecting plate 35a, 35a by mutual engaging are positioned, pushed down the inclined-plane 58a of the concave cam 58 of relief cam parts 47, so relief cam parts 47 are just by means of first centrifugal weight 35
1, remain on and make on the working position C that its convex cam 47a outwards protrudes from the basic circle of exhaust cam 26e.At this moment, if operation is used for the back springing type starting electrical machinery 13 of starting apparatus combustion engine E, because when by startup tube axle 12 bent axle 6 being rotated with starting electrical machinery 13, also driven camshaft 26 by timing transmission device 25, in the compression stroke of piston 7, with exhaust tappet 27e jack-up a little upwards, just by exhaust push rod 28e and exhaust rocker arm 29e, 17e opens a bit a little with exhaust valve by means of the convex cam 47a of relief cam parts 47.At this moment, the distribution of time as shown in figure 10.As a result, a part of pressurized gas in the cylinder barrel 3a is just discharged from relief opening 16e, has suppressed the rising of compression pressure, has therefore alleviated the operation load of starting electrical machinery 13, makes effectively starting more trippingly of bent axle 6, thus starting apparatus combustion engine at an easy rate.
In this process, because first centrifugal weight 35
1Be subjected to the setting load Fs of Returnning spring 53, just to second centrifugal weight 35
2To abutting part 35
2aPressurization makes second centrifugal weight 35
2Also remain on its retracted position J.
If behind the internal combustion engine start, the rotational speed N e of internal-combustion engine surpass to start the regional a of rotating speed, just as shown in figure 22, and the centrifugal weight 35 that produces because of centrifugal force Fw1
1The centrifugal weight 35 that produces around the moment of torsion of pivot 36 with because of centrifugal force Fw2
2Around the moment of torsion sum of pivot 36, surpassed because of setting 53 pairs of two centrifugal weights 35 of Returnning spring that load Fs is produced
1, 35
2Around the moment of torsion of pivot 36, make two centrifugal weights 35
1, 35
2Outer side oscillation from retracted position A, K towards radial direction respectively, first centrifugal weight 35
1Swing be delivered to connection bump 45c from connecting plate 35a, make driving ring 45 to counterclockwise rotating, and pin 45b moved towards the position relative with the bottom surface 58b of the concave cam 58 of relief cam parts 47.Therefore, relief cam parts 47 just are not subjected to the obstruction of pin 45b, move to inoperative position D under action of centrifugal force, and make its convex cam 47a retreat into the basic circle inboard of exhaust cam 26e.
In this process, as shown in figure 23, on exhaust gas recirculation cam part 48, because the bottom surface 59a of its concave cam 59 is relative with the pin 45b of driving ring 45, so exhaust gas recirculation cam part 48 just can not be subjected to the obstruction of pin 45b, remain on idle position F by means of centrifugal force, and make its convex cam 48a retreat into the basic circle inside of exhaust cam 26e.
As mentioned above, exhaust valve 17e only relies on the work of exhaust cam 26e to carry out switch control.And, when internal-combustion engine rotational speed Ne is in the low rotational speed region b of internal-combustion engine of Ne1～Ne2, still continue this state.Then, as Figure 22 and shown in Figure 23, when the rotational speed N e of internal-combustion engine reaches Ne2, second centrifugal weight 35
2Reach its front end is connected to expanded position K on the outer peripheral surface of wheel hub 32a, thereby limited it to the outer side shifting that surpasses this position.As a result, second centrifugal weight 35
2Centrifugal force Fw2 also just no longer Returnning spring 53 is produced resistances.Therefore, because first centrifugal weight 35
1The moment of torsion that produced around pivot 36 of centrifugal force Fw1, first centrifugal weight 35 that is produced with reposition force Fs because of Returnning spring 53
1Around the mutual balance of the moment of torsion of pivot 36, thereby determined first centrifugal weight 35
1The position, after this, with the rising of internal-combustion engine rotational speed Ne, first centrifugal weight 35
1Swing speed just slow down.
Then, when the rotational speed N e of internal-combustion engine surpasses Ne2, when internal-combustion engine E enters high rotational speed region C, just as shown in figure 24, first centrifugal weight 35
1The final expanded position B that arrives on the block 38 that is connected on the driven gear 32, meanwhile, because driving ring 45 is further to counterclockwise rotating, pin 45b just is pressed on the inclined-plane 59b of concave cam 59 of exhaust gas recirculation cam part 48, make exhaust gas recirculation cam part 48 overcome its centrifugal force, move on the G of working position, so exhaust gas recirculation cam part 48 just makes its convex cam 48a protrude from the basic circle of exhaust cam 26e.Therefore, in the aspirating stroke of piston 7, by means of the convex cam 48a of exhaust gas recirculation cam part 48 with exhaust tappet 27e a little upwards jack-up a bit just can open exhaust valve 17e a bit a little by exhaust push rod 28e and exhaust rocker arm 29e.As a result, the waste gas that remains in relief opening 16e place just can be inhaled in the firing chamber 15, has promptly carried out exhaust gas recirculation.These waste gas in the expansion stroke in stage during mixture combustion, can suppress the excessive rising of combustion temperature afterwards, in the NOx concentration, can also reduce the concentration of HC in reducing waste gas, help improving its low fuel consumption performance.
As mentioned above, in this 3rd embodiment, by means of first and second centrifugal weights of swinging along with the raising of internal-combustion engine rotational speed Ne 35
1, 35
2, and the Returnning spring 53 that elastic force is opposite with this swing, just can carry out work successively by shared driving ring 45, and, by selected second centrifugal weight 35 that makes
2Time of operational failure, just can freely set the working zone of exhaust gas recirculation cam part 48, and it is irrelevant with the working zone of relief cam parts 47, therefore, as long as on valve gear 20, increase simple structure, cheap valve gear 20 just can be provided, and this valve gear 20 has the pressure-reducing function and the exhaust gas recirculation function of the desirable characteristic of mutual noninterference.
The utility model is not limited in the foregoing description, in the scope that does not break away from the utility model design, can carry out many variations to its design.For example, in first and second embodiments, can be nonlinear spring with an elasticity coefficient, substitute first and second Returnning springs 43,44.
Claims (6)
1. the valve gear of an internal-combustion engine, it has following various parts: with the camshaft (26) of bent axle (6) interlock; Can open and close the intake cam driven member (27i) and the exhaust cam driven member (27e) of intake valve (17i) and exhaust valve (17e), this intake cam driven member (27i) and exhaust cam driven member (27e) are provided with in linkage with the intake cam (26i) and the exhaust cam (26e) that are arranged on this camshaft (26) respectively; It is characterized in that,
Also have following various parts: relief cam parts (47), its can be between working position (C) and inoperative position (D) along being arranged on the above-mentioned camshaft (26) of above-mentioned camshaft (26) with radially sliding, have the convex cam (47a) of the pinnacle part that is lower than above-mentioned exhaust cam (26e) on the outer peripheral surface of above-mentioned relief cam parts (47); Above-mentioned relief cam parts (47) one sides and above-mentioned camshaft (26) connect, and above-mentioned convex cam (47a) protrudes from the basic circle of above-mentioned exhaust cam (26e), and this exhaust cam driven member (27e) is positioned at the working position of opening exhaust valve (17e); The opposite side of above-mentioned relief cam parts (47) and above-mentioned camshaft (26) connect, and above-mentioned convex cam (47a) is positioned at the basic circle inboard of above-mentioned camshaft (26), and this exhaust cam driven member (27e) is positioned at the inoperative position of unclamping;
Exhaust gas recirculation cam part (48), it can have the convex cam (48a) of the pinnacle part that is lower than above-mentioned exhaust cam (26e) along being arranged on the above-mentioned camshaft (26) of above-mentioned camshaft (26) with radially sliding on the outer peripheral surface of above-mentioned exhaust gas recirculation cam part (48); Above-mentioned exhaust gas recirculation cam part (48) one sides and above-mentioned camshaft (26) connect, and above-mentioned convex cam (48a) protrudes from the basic circle of above-mentioned exhaust cam (26e), and this exhaust cam driven member (27e) is positioned at the working position of opening exhaust valve (17e); The opposite side of above-mentioned exhaust gas recirculation cam part (48) and above-mentioned camshaft (26) connect, and above-mentioned convex cam (48a) is positioned at the basic circle inboard of above-mentioned camshaft (26), and this exhaust cam driven member (27e) is positioned at the inoperative position of unclamping;
Shared centrifugal mechanism (46) is provided with above-mentioned camshaft (26) interlock.
2. the valve gear of internal-combustion engine as claimed in claim 1 is characterized in that,
Above-mentioned centrifugal mechanism (46) is made of following parts:
Centrifugal weight (35; 35
1, 35
2), can to radial direction swingingly pivot suspension be fixedly installed on the support unit (32) on the above-mentioned camshaft (26);
To this centrifugal weight (35; 351,352) apply the Returnning spring (43,44 of elastic force to the inboard of radial direction; 53), its at least one end and above-mentioned centrifugal weight (35; 351,352) be connected;
And with above-mentioned centrifugal weight (35; The common driver part (45) of swing interlock 351,352), its respectively be arranged on above-mentioned relief cam parts (47) and exhaust gas recirculation cam part (48) on cam (58,59) engage, and be provided with in linkage with above-mentioned relief cam parts (47) and above-mentioned exhaust gas recirculation cam part (48).
3. the valve gear of internal-combustion engine as claimed in claim 2 is characterized in that,
Above-mentioned Returnning spring is made of first Returnning spring (43) and second Returnning spring (44), the movable end (43a) of above-mentioned first Returnning spring (43) is connected with the first movable attachment portion (40) of the intermediate portion of above-mentioned centrifugal weight (35), and the movable end (44a) of above-mentioned second Returnning spring (44) is connected with the second movable attachment portion (41) on the swing end of above-mentioned centrifugal weight (35).
4, the valve gear of internal-combustion engine as claimed in claim 2, it is characterized in that: above-mentioned Returnning spring is made of first Returnning spring (43) and second Returnning spring (44), and the movable end (43a) of above-mentioned first Returnning spring (43) is connected with the first movable attachment portion (40) of the intermediate portion of above-mentioned centrifugal weight (35); Above-mentioned second Returnning spring (44) is made of torsion-coil spring, and be set on the pivot of above-mentioned centrifugal weight (35), the above-mentioned pivot of first and second arms of above-mentioned second Returnning spring (44) (44c, 44d) clamping, and fastening is at first and second baffle plates (62,63) that are formed on the centrifugal weight (35).
5. the valve gear of internal-combustion engine as claimed in claim 2 is characterized in that,
Above-mentioned centrifugal weight is made of first centrifugal weight (351) and second centrifugal weight (352), and above-mentioned Returnning spring (53) is arranged between above-mentioned first centrifugal weight (351) and the above-mentioned support unit (32); Above-mentioned centrifugal weight (351) has the inner side surface with the above-mentioned support unit of butt (32), and the outer side surface that connects with the block (38) that is arranged on the above-mentioned support unit (32); And above-mentioned first centrifugal weight (351) and second centrifugal weight (352) but between slide relative ground be provided with.
6, as the valve gear of the arbitrary described internal-combustion engine of claim 2 to 5, it is characterized in that: above-mentioned centrifugal weight (35,351) has the inner side surface that the wheel hub (32a) with above-mentioned support unit (32) connects, and the outer side surface that connects with the block (38) that is arranged on the above-mentioned support unit (32).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004016953 | 2004-01-26 | ||
| JP2004016953 | 2004-01-26 | ||
| JP2004152424 | 2004-05-21 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2841989Y true CN2841989Y (en) | 2006-11-29 |
Family
ID=35519552
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2005200033393U Expired - Lifetime CN2841989Y (en) | 2004-01-26 | 2005-01-26 | Valve operating system for internal combustion engine |
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| Country | Link |
|---|---|
| CN (1) | CN2841989Y (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101852111A (en) * | 2009-03-31 | 2010-10-06 | 本田技研工业株式会社 | The variable driving valve device of motor |
| CN102365448A (en) * | 2009-04-08 | 2012-02-29 | 三菱重工业株式会社 | Cam for lifting/lowering exhaust valve, 4-cycle engine equipped with supercharger, and method for controlling valve timing |
| CN101397955B (en) * | 2007-09-28 | 2012-05-30 | 本田技研工业株式会社 | Exhaust gas recirculation device |
| CN101713312B (en) * | 2008-09-30 | 2012-06-20 | 本田技研工业株式会社 | A variable stigmatic opening transmission device of an engine |
-
2005
- 2005-01-26 CN CNU2005200033393U patent/CN2841989Y/en not_active Expired - Lifetime
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101397955B (en) * | 2007-09-28 | 2012-05-30 | 本田技研工业株式会社 | Exhaust gas recirculation device |
| CN101713312B (en) * | 2008-09-30 | 2012-06-20 | 本田技研工业株式会社 | A variable stigmatic opening transmission device of an engine |
| CN101852111A (en) * | 2009-03-31 | 2010-10-06 | 本田技研工业株式会社 | The variable driving valve device of motor |
| CN102365448A (en) * | 2009-04-08 | 2012-02-29 | 三菱重工业株式会社 | Cam for lifting/lowering exhaust valve, 4-cycle engine equipped with supercharger, and method for controlling valve timing |
| CN102365448B (en) * | 2009-04-08 | 2014-03-12 | 三菱重工业株式会社 | Cam for lifting/lowering exhaust valve, 4-cycle engine equipped with supercharger, and method for controlling valve timing |
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Effective date of abandoning: 20071121 |
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