CN100532793C - Decompression mechanism - Google Patents
Decompression mechanism Download PDFInfo
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- CN100532793C CN100532793C CNB2006101427175A CN200610142717A CN100532793C CN 100532793 C CN100532793 C CN 100532793C CN B2006101427175 A CNB2006101427175 A CN B2006101427175A CN 200610142717 A CN200610142717 A CN 200610142717A CN 100532793 C CN100532793 C CN 100532793C
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- camshaft
- slider
- decompressor
- cam
- force
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- 230000007246 mechanism Effects 0.000 title claims abstract description 99
- 230000006837 decompression Effects 0.000 title 1
- 230000002093 peripheral effect Effects 0.000 claims abstract description 16
- 230000002265 prevention Effects 0.000 claims description 3
- 230000006835 compression Effects 0.000 description 27
- 238000007906 compression Methods 0.000 description 27
- 238000010304 firing Methods 0.000 description 7
- 230000015572 biosynthetic process Effects 0.000 description 6
- 238000012423 maintenance Methods 0.000 description 5
- 238000002485 combustion reaction Methods 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 238000003780 insertion Methods 0.000 description 2
- 230000037431 insertion Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000002452 interceptive effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- FTKOCAZZFUDHDQ-OXLBYMFNSA-N α-cam Chemical compound C([C@@H](N(CC1)C)C23C=C[C@@]4([C@H](C3)CN(CCCl)CCCl)OC)C3=CC=C(O)C5=C3[C@@]21[C@H]4O5 FTKOCAZZFUDHDQ-OXLBYMFNSA-N 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/08—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for decompression, e.g. during starting; for changing compression ratio
- F01L13/085—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for decompression, e.g. during starting; for changing compression ratio the valve-gear having an auxiliary cam protruding from the main cam profile
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- High-Pressure Fuel Injection Pump Control (AREA)
Abstract
The invention provides a decompressing mechanical with simplified structure and capable of being miniaturized. The decompressing mechanism 70 comprises a centrifugal regulator 80 fitted on the camshaft 50 of the engine 10, a sliding part 81 moved along the axial direction of the camshaft 50 by the centrifugal force of the centrifugal balance weight 82, a decompressing cam 87 integrally arranged with the sliding part 81 of the centrifugal regulator 80, and a force applying member 95 arranged between the peripheral of the camshaft 50 and the inner surrounding part and applying a force on the sliding part 81 in the moving direction of the sliding part to conquer the centrifugal force to damp the moving of the sliding part 81.
Description
Technical field
The present invention relates to a kind of mechanism of decompressor that when engine start, lowers the compression pressure of motor.
Background technique
At present, lowering the mechanism of decompressor (mechanism of decompressor during starting) of the compression pressure of motor when engine start, has been known technology.In this mechanism of decompressor, distolateral hole, big footpath that is provided with at camshaft, in this hole, big footpath, dispose guide rod, on this guide rod, be arranged with the sliding type relief cam vertically and to the spring of this relief cam application of force, and outboard shafts is supported with the governor weight (for example, patent documentation 1) that relief cam is moved around relief cam.
In addition, in the mechanism of decompressor, on camshaft, be arranged with vertically relief cam, camshaft move axially and can with the housing of relief cam engagement, to the force application device of this housing application of force and housing is moved so as with the governor weight (for example, patent documentation 2) of relief cam engagement.
Patent documentation 1: No. 2746985, Japan's special permission;
Patent Document 2: the real fair 2-23770 communique of Japan.
But, in the scheme of above-mentioned patent documentation 1 record, owing to axially dispose sliding type relief cam and spring etc. in turn along camshaft, so caused the total length (cam shaft to length) of the mechanism of decompressor elongated, in addition, owing to the governor weight axle is supported in the hole, big footpath of camshaft, so structure complicated with bearing pin, component number increases, and causes mechanism of decompressor diameter to increase.
And, in the scheme of above-mentioned patent documentation 2 records, because axially-aligned relief cam, housing (being equivalent to slider) and force application device etc. along camshaft, so also caused the total length of the mechanism of decompressor elongated, in addition, owing to make relief cam and housing engagement, so the engaging pawl need be set respectively, thereby complex-shapedization of these parts simultaneously, adopts meshing engagement structure can cause the mechanism of decompressor complicated.
Summary of the invention
The present invention In view of the foregoing proposes, and its purpose is to provide the mechanism of decompressor of the simple and Miniaturizable of a kind of mechanism.
In order to address the above problem, the invention is characterized in, in the mechanism of decompressor, comprise: centrifugal governor, it is arranged on the camshaft of motor, and has by the centrifugal force of governor weight along the axially movable slider of this camshaft; Relief cam, the slider of itself and this centrifugal governor is provided with integratedly; And force application part, it is arranged between the interior perimembranous of the peripheral part of described camshaft and described slider, and overcome described centrifugal force with the direction that stops described slider and move on to the described slider application of force; Wherein, described force application part is by described slider and described camshaft clamping.
According to the present invention, owing to have the relief cam that the slider with centrifugal governor is provided with integratedly; And be arranged between the interior perimembranous of the peripheral part of camshaft and slider, and overcome centrifugal force with the direction that stops slider and move on to the force application part of the slider application of force, so, compare with the structure of outside configuration governor weight around relief cam with the structure of the spring that the slider application of force is used with axially-aligned slider along camshaft, can reduce the number of parts, and the cam shaft that can shorten the mechanism of decompressor to total length, simultaneously, can realize reducing of mechanism of decompressor diameter.In addition, owing to do not need to be provided with the engagement formation that makes slider and relief cam engagement, thus can avoid the complicated of component shape, thus realize the simplification of the mechanism of decompressor.And, according to this structure, do not need parts that force application part is positioned, keeps, can reduce the number of parts.
In this case, preferably described camshaft is provided with outstanding mobile prevention parts to stop described slider to move at the circumferencial direction of camshaft.According to this structure, can stop parts to make slider and the rotation of integrated camshaft ground by moving.
In this case, preferred described slider has integratedly and runs through the tube portion that is inserted on the camshaft periphery and extend the lip part that is provided with and described governor weight is led at the peripheral part of this one, and described force application part is configured in the interior week of described tube portion.
In addition, also the arm with described relief cam butt can be arranged on the exhaust valve rocker arm.According to this structure, this mechanism of decompressor can be applied on valve mechanism, be provided with in the motor of rocking arm.
The mechanism of decompressor of the present invention comprises: the relief cam that is provided with integratedly with the slider of centrifugal governor; And be arranged between the interior perimembranous of the peripheral part of camshaft and slider, and overcome centrifugal force with the direction that stops slider and move on to the force application part of the slider application of force, so, can reduce the number of parts, and the cam shaft that can shorten the mechanism of decompressor to total length, simultaneously, can realize reducing of mechanism of decompressor diameter.In addition, owing to do not need to be provided with the engagement formation that makes slider and relief cam engagement, thus can avoid the complicated of component shape, thus the mechanism of decompressor is oversimplified.In addition, the present invention is owing to come the clamping force application part by slider and camshaft, thus do not need parts that force application part is positioned, keeps, thus can reduce the number of parts.
In addition, the present invention is because camshaft is provided with outstanding mobile prevention parts to stop slider to move to the circumferencial direction of camshaft, so slider and integrated camshaft ground are rotated.
In addition, the present invention is owing to will be arranged on the exhaust valve rocker arm with the arm of relief cam butt, so, this mechanism of decompressor can be applied on valve mechanism, be provided with in the motor of rocking arm.
Description of drawings
Fig. 1 is the sectional side view of motor with mechanism of decompressor of the 1st mode of execution.
Fig. 2 is II-II sectional drawing of Fig. 1.
(a) among Fig. 3 is the plan view of mechanism of decompressor slider, (b) is the sectional drawing of slider, (c) is the rear view of slider.
(a) among Fig. 4 is the plan view that the counterweight of the mechanism of decompressor keeps body, (b) is the sectional drawing that counterweight keeps body, (c) is the rear view that counterweight keeps body.
The schematic representation of the mechanism of decompressor among (a) the compression stroke α when being engine start among Fig. 5, the schematic representation of the mechanism of decompressor when (b) being engine start in other strokes.
(a) among Fig. 6 is the schematic representation of the mechanism of decompressor among the compression stroke α after the engine start, (b) is the schematic representation of the mechanism of decompressor in other strokes after the engine start.
Fig. 7 is the sectional drawing of part that the motor of the mechanism of decompressor that adopts the 2nd mode of execution is shown.
The schematic representation of (a) mechanism of decompressor when being engine start among Fig. 8 (b) is the schematic representation of the mechanism of decompressor after the engine start.
Label declaration:
10 motors; 22 pistons;
35 intake valves;
36 exhaust valves;
40 valve mechanisms;
45 intake cams;
46 exhaust cams;
47,48 bearings;
50 camshafts;
55 inlet valve rockers;
56 exhaust valve rocker arms;
60 timing driving mechanisms;
70,200 mechanisms of decompressor;
80,100 centrifugal governors;
81,101 sliders;
82 governor weights;
83,103 counterweights keep body;
87,107 relief cams;
90,110 card shotpins (move and stop parts);
95,115 force application parts;
118 ring portions.
Embodiment
Below, with reference to accompanying drawing embodiments of the present invention are described.
Fig. 1 is the sectional side view of the motor of lift-launch on the automotive bicycle of minitype motorcycle type vehicle etc. with mechanism of decompressor of present embodiment.This motor 10 is single cylinder four stroke engine, and it has crankcase 11, cylinder block 12, reaches cylinder head 13.In crankcase 11 upper supports bent axle 20 is arranged, and make these bent axle 20 rotations freely; Be formed with cylinder 23 on cylinder block 12, the piston 22 that is connected with bent axle 20 by connecting rod 21 slides in cylinder 23.In addition, on bent axle 20, be equipped with the counterweight 20A that is used to obtain spin balancing.
As shown in Figure 2, valve mechanism 40 has the camshaft 50 of bringing gas cam 45 and exhaust cam 46 into.This camshaft 50 is supported on the cylinder head 13 by pair of bearings 47,48 in the mode at middle clamping intake cam 45 and exhaust cam 46, and this camshaft 50 can rotate freely.As shown in Figures 1 and 2, in the gap between this camshaft 50 and valve mechanism cover 14, be supported with the inlet valve rocker 55 and exhaust valve rocker arm 56 that can freely swing; Inlet valve rocker 55 one ends and intake cam 45 butts, the head butt of the other end and intake valve 35; Exhaust valve rocker arm 56 one ends and exhaust cam 46 butts, the head butt of the other end and exhaust valve 36.
As shown in Figure 1, intake valve 35 and exhaust valve 36 are stressed to the direction of closing each mouthful 31,32 by each valve spring 37, each 35,36 35,36 opens each by downward pushing for above-mentioned inlet valve rocker 55 and exhaust valve rocker arm 56, thereby each mouthful 31,32 is communicated with firing chamber 30.In case when not pushing downwards, under the effect of the counter-force of each valve spring 37, door 35,36 is closed, thereby cut off being communicated with of each mouthful 31,32 and firing chamber 30.In addition, on cylinder head 13, be equipped with supplying to the spark plug 38 (Fig. 2) of the mixed gas igniting usefulness in the firing chamber 30.
As shown in Figure 2, above-mentioned camshaft 50 is connected on the bent axle 20 by timing driving mechanism 60.Timing driving mechanism 60 is configured in the timing Transmission Room 60H, and this timing Transmission Room 60H extends from the side direction of cylinder head 13 below, through cylinder block 12 and with crankcase 11 in are communicated with; This timing driving mechanism 60 has the driven sprocket 61 that is fixed on camshaft 50 1 ends, be fixed on driving sprocket wheel (not shown) on the bent axle 20 and volume hangs over annular timing chain (not shown) on two sprocket wheels, thereby this timing driving mechanism 60 can pass to camshaft 50 with 1/2nd reduction speed ratio with the rotation of bent axle 20.In addition, this timing driving mechanism 60 is not limited to above-mentioned chain driving mode, also can adopt the gear transmission mode that the rotation of bent axle 20 is passed to camshaft by a plurality of gears.
By this timing driving mechanism 60, rotate between two refundings at bent axle 20, camshaft 50 rotates a circle, and, when intake valve 35 opened and closed along with the cam profile of intake cam 45 by the rotation of this camshaft 50, exhaust valve 36 was along with the cam profile of exhaust cam 46 opens and closes.
More particularly, by the rotation of above-mentioned camshaft 50, piston 22 from upper dead center to lower dead centre carry out downwards moving during, have only intake valve 35 to open (intake stroke); Then, piston 22 from lower dead centre to upper dead center be moved upward during, intake valve 35 and exhaust valve 36 are closed (compression stroke); Then, once more piston 22 from upper dead center to lower dead centre carry out downwards moving during, intake valve 35 and exhaust valve 36 keep closed conditions (combustion stroke); At last, piston 22 from lower dead centre during upper dead center moves, have only exhaust valve 36 to open (exhaust stroke).That is, can carry out each stroke of four stroke engine, i.e. Men switching.In addition, figure 1 illustrates piston 22 moves with from the state of compression stroke (representing with symbol) when combustion stroke switches to upper dead center (shown in the solid line) from lower dead centre (shown in the double dot dash line).
Yet, piloted engine 10 o'clock, as if in above-mentioned compression stroke α, intake valve 35 and exhaust valve 36 keep original closed condition, then cause the rotation of bent axle 20 seriously to be arrived and the piston 22 compression cylinders 23 interior suitable amounts of air (or mixed gas) that reach in the firing chamber 30.Therefore, adopt in the engine start mode under the situation of accumulator drive mode, particularly under the situation of the high motor of the motor of big air displacement or compression ratio, need starting motor to maximize; In addition, under the situation that adopts the Kick-start mode, need stronger recoil force.
Thereby, in the present embodiment, on camshaft 50, dispose the mechanism of decompressor 70 of opening exhaust valve 36 among the compression stroke α when engine start, the compression pressure in the time of can lowering engine start by this mechanism of decompressor 70.
The mechanism of decompressor 70 has the centrifugal governor 80 that makes the mechanism of decompressor 70 actions by the rotating force of camshaft 50 as shown in Figure 2; This centrifugal governor 80 is configured between the bearing 48 of the exhaust cam 46 of camshaft 50 and supporting cam wheel axle 50.This centrifugal governor 80 has: can run through being inserted on the camshaft 50 and moving axially freely slider 81 along it; Run through be inserted on the camshaft 50 and and slider 81 between maintain a plurality of governor weights (ball shape) 82 counterweight keep body 83.
Shown in Fig. 3 (a) and (b), (c), slider 81 has integratedly: run through the tube portion 85 that is inserted on the camshaft 50; Peripheral part in this one 85 extends the lip part 86 that is provided with; And go up devices spaced apart and the relief cam 87 that disposes at axially (=the camshaft 50 axially) of tube portion 85 with respect to this lip part 86.
Shown in Fig. 3 (b), tube portion 85 roughly has drum, and interior perimembranous 88 form side-prominent interior all protuberance 88A of inside week with relief cam 87 opposite sides, the value that the outer diameter D 1 (Fig. 2) of the supporting portion that the inner diameter d 1 of all protuberance 88A is supported with the bearing 48 with camshaft 50 in this forms the roughly the same diameter of Spielpassung forms.
In addition, the inner diameter d 2 of the part except that interior all protuberance 88A of tube portion 85 with the exhaust cam 46 of camshaft 50 near the outer diameter D 2 (D2〉D1, with reference to Fig. 2) of the part value that forms the roughly the same diameter of Spielpassung form; Shown in Fig. 3 (a),, form slot part 89A with the intervals of 180 degree with respect to the central shaft C1 of tube portion 85 in this part.This slot part 89A from the end face of relief cam 87 sides of tube portion 85 to outside opening.
As shown in Figure 2, this slider 81 is inserted on the camshaft 50 in the mode that is inserted in respectively the above-mentioned slot part 89A from camshaft 50 outstanding two ends that runs through the card shotpin (move and stop parts) 90 that is inserted on the camshaft 50, thus, slider 81 is configured in with can move freely camshaft 50 axially in, stop sliders 81 to the moving of the circumferencial direction of camshaft 50 by means of card shotpin 90, thereby slider 81 and camshaft 50 are rotated integratedly.
Above-mentioned arm 56A has from exhaust valve rocker arm 56 and extends the shape of extending again downwards to the side as shown in Figure 2, and is configured in not the position of interfering with exhaust cam 46.This arm 56A is upwards pushed the end with the exhaust valve rocker arm 56 of arm 56A one by the last pushed section 87A butt with relief cam 87, then the other end of exhaust valve rocker arm 56 be urged downwardly, thereby exhaust valve 36 is unlocked.
In addition, this arm 56A can be integrally formed with exhaust valve rocker arm 56, also can be connected with exhaust valve rocker arm 56 with independent parts manufacturing in addition again.
Counterweight keeps body 83 as Fig. 4 (a) and (b), (c) shown in, is the annular plate parts that central authorities have through hole 83A, and the inner diameter d 3 of this through hole 83A is with the diameter value formation roughly the same with the outer diameter D 1 of camshaft 50.As shown in Figure 2, this counterweight keep body 83 above-mentioned slider 81 run through be inserted on the camshaft 50 after, be sleeved on again on this camshaft 50; Contact with the inner ring of a bearing 48 of supporting cam wheel axle 50 around the through hole 83A, the outside of this inner ring contacting part 83B forms towards the oblique rake 83C of slider 81 inclinations, and this counterweight maintenance body 83 is formed the shape that only contacts with the inner ring of bearing 48.
Between the lip part 86 of this rake 83C and slider 81, along the peripheral direction of camshaft 50 with (30 degree at interval) configuration governor weight 82 uniformly-spaced.As shown in Figure 2, the lip part 86 of this rake 83C and slider 81 is owing to form to the approaching more each other shape of the peripheral direction of camshaft 50, so, even governor weight 82 moves to centrifugal direction under the action of centrifugal force of the rotation generation of camshaft 50, the lip part 86 that also can be tilted 83C of portion and slider 81 clamps, thereby can not be shed to the outside.In addition, rotate the state that on governor weight 82, acts on centrifugal force, in other words, show the state in the engine running thereby Fig. 2 shows camshaft.
Here, as shown in Figure 2, between the peripheral part of the interior perimembranous of above-mentioned slider 81 and camshaft 50, dispose the force application part 95 of this slider 81 towards the opposite direction application of force of exhaust cam 46.This force application part 95 adopts helical spring, stepped part 92 butts of the part of the outer diameter D 2 of one end and camshaft 50 and the part of outer diameter D 1 (D2〉D1), the stepped part butt of interior all protuberance 88A of the other end and slider 81, thus, by slider 81 and camshaft 50 clampings, and along camshaft 50 axially to the opposite direction application of force of slider 81 towards exhaust cam 46.
Below, the assembling sequence of this mechanism of decompressor 70 is described with reference to Fig. 2.In addition, as prerequisite, this mechanism of decompressor 70 is being assembled on the camshaft 50 before the assembling of bearing 48.At first, will block shotpin 90 and run through and be inserted in the camshaft 50, and simultaneously, force application part 95 be run through being inserted on the camshaft 50, under this state, from a distolateral insertion slider 81 of camshaft 50, and the two ends that will block shotpin 90 are inserted in the slot part 89A of this slider 81.Then, from distolateral running through of camshaft 50 plugging counterweight maintenance body 83, and governor weight 82 is configured between the lip part 86 of this counterweight maintenance body 83 and slider 81, and, bearing 48, liner 49, driven sprocket 61 and flange 62 are installed on camshaft 50 in turn.Like this, only on camshaft 50, insert each parts that constitutes the mechanism of decompressor 70 in turn, just can easily assemble the mechanism of decompressor 70.
The following describes the action of the mechanism of decompressor 70.The schematic representation of the mechanism of decompressor 70 when Fig. 5 (a) and (b) are the expression engine start.In addition, Fig. 5 (a) shows the situation that motor 10 carries out compression stroke α, and Fig. 5 (b) shows the situation that motor 10 carries out compression stroke α action in addition.
During engine start, camshaft 50 is roughly zero with utmost point low speed rotation or revolution, in this case, owing to almost do not produce centrifugal force on the governor weight 82, so, slider 81 is under the effect of the elastic force of force application part 95, opposite direction towards exhaust cam 46 moves, move by this, governor weight 82 keeps the rake 83C of body 83 to interior all side shiftings along the plane of inclination 86A and the counterweight of the lip part 86 of slider 81, thereby slider 81 with move to this and stop on position of governor weight 82 butts of interior all sides (below, be called the 1st position).
The 1st position is equivalent to be arranged on relief cam 87 position relative with the arm 56A of exhaust valve rocker arm 56 on the slider 81 shown in Fig. 5 (a) and (b).Thereby, carry out under the situation of compression stroke α at motor 10, shown in Fig. 5 (a), the last pushed section 87A of relief cam 87 will upwards promote with the exhaust valve rocker arm 56 of arm 56A one, make exhaust valve rocker arm 56 upwards float gap delta, thereby open exhaust valve 36 from exhaust cam 46.
On the other hand, under the situation of the action beyond motor 10 carries out compression stroke α, shown in Fig. 5 (b), the last pushed section 87A of relief cam 87 not with arm 56A butt, and exhaust valve rocker arm 56 remains on the state with exhaust cam 46 butts, thereby along with the cam profile of exhaust cam 46 opens and closes exhaust valve 36.
The action of the mechanism of decompressor 70 of (after the engine start) when the revolution of camshaft 50 rises then, is described from above-mentioned state.Here, Fig. 6 (a) and (b) are figure of the mechanism of decompressor 70 after the expression engine start, and Fig. 6 (a) shows the situation that motor 10 carries out compression stroke α, and Fig. 6 (b) shows the situation that motor 10 carries out compression stroke α action in addition.
When camshaft 50 from serving as that zero state begins revolution when rising with utmost point low speed rotation or revolution, the centrifugal force that acts on the governor weight 82 becomes big, and the centrifugal action of governor weight 82 is on the plane of inclination 86A of the lip part 86 of slider 81, therefore, generation makes the power of slider 81 to exhaust cam 46 side shiftings, and when this power surpasses the elastic force of force application part 95, slider 81 overcomes the elastic force of force application part 95, to exhaust cam 46 side shiftings, thus as Fig. 6 (a), (b) shown in, slider 81 moves to and the position of exhaust cam 46 butts (below, be called the 2nd position).
The 2nd position is equivalent to be arranged on relief cam 87 position that standby is evaded in the arm 56A of exhaust valve rocker arm 56 and the gap between the exhaust cam 46 on the slider 81, in other words, is equivalent to not the non-butt position with arm 56A butt.Thereby, after the engine start, no matter any one that motor 10 carries out in compression stroke α, combustion stroke, exhaust stroke and the intake stroke, shown in Fig. 6 (a) and (b), exhaust valve rocker arm 56 all can with exhaust cam 46 butts, thereby open and close exhaust valve 36 along with the cam profile of exhaust cam 46.
Therefore,, only when engine start, in the compression stroke α of motor 10, open exhaust valve 36 by the above-mentioned mechanism of decompressor 70, thus the compression pressure when lowering engine start.Thereby, adopt in the engine start mode under the situation of accumulator drive mode, compare with the situation that the mechanism of decompressor is not set, can adopt small-sized starting motor, in addition, under the situation that adopts the Kick-start mode, can reduce the needed recoil force of engine start, make engine start easily.
In the present embodiment, the above-mentioned mechanism of decompressor 70 has centrifugal governor 80, this centrifugal governor 80 has and runs through the slider 81 that is inserted on the camshaft 50, run through be inserted on the camshaft 50 and and slider 81 between keep the counterweight of a plurality of governor weights 82 to keep body 83, and, between the peripheral part of the interior perimembranous of this slider 81 and camshaft 50, dispose force application part 95 to this slider 81 application of forces, therefore, compare with conventional art along the spring that axially disposes slider in turn and the slider application of force is used of camshaft, the cam shaft that can shorten the mechanism of decompressor 70 to total length.
In addition, in this structure, because by slider 81 and camshaft 50 clamping force application parts 95, so, do not need the parts that force application part 95 is positioned, keeps; In addition,,, can reduce the number of parts so compare with the technology that relief cam is made independent parts with slider in the past because slider 81 forms with relief cam 87, therefore, the cam shaft that can shorten the mechanism of decompressor 70 to total length.In addition, owing to do not need as in the past, to be provided with the engagement formation that makes slider and relief cam engagement, so, can avoid the complicated of component shape, the mechanism of decompressor is oversimplified.
Further, in this structure, because remaining on, governor weight 82 runs through between the slider 81 and counterweight maintenance body 83 that is inserted on the camshaft 50, so, with distolaterally hole, big footpath is set and in this hole, big footpath, disposes guide rod at one of camshaft, and at this guide rod upper edge axial arrangement relief cam and spring, outboard shafts supports the technology of the governor weight that relief cam moves is compared around it, do not need axle to support the parts of governor weight, thereby can realize that the component number purpose further reduces and the simplification of mechanism, and owing to do not need governor weight is configured in the outside on every side of relief cam, so can realize reducing of mechanism of decompressor diameter.
Thus, the mechanism of decompressor 70 of this structure can be realized the miniaturization and the light of all shapes.Therefore, by adopting this mechanism of decompressor 70, can realize attenuating and the miniaturization of cylinder head 13 and the light around the cylinder head 13 of the rotary load of motor 10.
(2) the 2nd mode of executions
Fig. 7 and Fig. 8 (a) and (b) show the 2nd mode of execution.
Show the mechanism of decompressor 200 in this embodiment, this mechanism of decompressor 200 disposes the force application part 115 of this slider 101 to the exhaust cam 46 side application of forces in the inboard of slider 101, in case and with motor 10 starting, slider 101 just constitutes centrifugal governor 100 along camshaft 50 to the mode that the opposition side of exhaust cam 46 moves.In addition, for convenience of explanation,, and omit its detailed description to the identical symbol of parts mark identical with the 1st mode of execution.
As shown in Figure 7, centrifugal governor 100 has: run through being inserted on the camshaft 50 and moving along its axis freely slider 101; Run through be inserted on the camshaft 50 and and slider 101 between keep the counterweight of a plurality of governor weights (ball shape) 82 to keep body 103.
In addition, interior all diameters of lip part 106 sides of tube portion 105 form greatlyyer than all diameters in other.Therefore, as shown in Figure 7, tube portion 105 is being run through under the situation about being inserted on the camshaft 50, and be formed for disposing the configuration space 116 of force application part 115 between this one 105 and the camshaft 50.This force application part 115 for example adopts helical spring, be configured in an end of the force application part 115 in the configuration space 116 and wall portion 117 butts of configuration space 116 inboards, the other end and be inserted in slider 101 and the bearing 48 of supporting cam wheel axle 50 between ring portion 118 butts.
Counterweight keeps body 103 to have the general cylindrical shape shape that can freely insert slider 101, more particularly, its internal diameter have can be fixed on ring portion 107A on the slider 101 and form the diameter of Spielpassung, simultaneously, have the opening 103B that the cam part 107B that can make the slider 101 that is inserted passes through, also further be provided with integratedly and running through under the state that is inserted on the camshaft 50 to the oblique rake 103C of bearing 48 inclinations.
The assembling of this mechanism of decompressor 200 is that at first, the insertion counterweight keeps after the body 103 on camshaft 50, is inserted in slider 101 on the camshaft 50 and is inserted into counterweight to keep in the body 103; Then, force application part 115 is inserted in the configuration space 116 of this slider 101 after, ring portion 118 is inserted on the camshaft 50, thereby just the mechanism of decompressor 200 is assembled on the camshaft 50.
The following describes the action of the mechanism of decompressor 200.The mechanism of decompressor 200 of Fig. 8 (a) when showing engine start, Fig. 8 (b) shows the mechanism of decompressor 200 after the engine start.
During engine start, camshaft 50 is roughly zero with utmost point low speed rotation or revolution, in this case, owing to almost do not produce centrifugal force on the governor weight 82, so, slider 101 is under the effect of the elastic force of force application part 115, towards exhaust cam 46 side shiftings, move by this, governor weight 82 keeps the rake 103C of body 103 to interior all side shiftings along the lip part 106 and the counterweight of slider 101, and slider 101 with move to this and stop on position of governor weight 82 butts of interior all sides (below, be called the 1st position).
The 1st position is equivalent to be arranged on relief cam 107 position relative with the arm 56A of exhaust valve rocker arm 56 on the slider 101 shown in Fig. 8 (a).Thereby, carry out under the situation of compression stroke α at motor 10, shown in Fig. 8 (a), the last pushed section 87A of relief cam 107 will upwards promote with the exhaust valve rocker arm 56 of arm 56A one, make exhaust valve rocker arm 56 upwards float gap delta, thereby exhaust valve 36 is unlocked from exhaust cam 46.On the other hand, under the situation of the action beyond motor 10 carries out compression stroke α, the last pushed section 87A of relief cam 107 not with arm 56A butt, and exhaust valve rocker arm 56 and exhaust cam 46 butts, and open and close exhaust valve 36 along with the cam profile of exhaust cam 46.
In addition, when serving as that zero state begins revolution when rising with utmost point low speed rotation or rotating speed from camshaft 50, the centrifugal force that acts on the governor weight 82 becomes big, the centrifugal action of governor weight 82 keeps on the rake 103C of body 103 in counterweight, produce the power that slider 101 is moved to the opposition side of exhaust cam 46 thus, and when this power surpasses the elastic force of force application part 115, slider 101 overcomes the elastic force of force application part 115, opposition side to exhaust cam 46 moves, therefore, shown in Fig. 8 (b), slider 101 moves to and the position of ring portion 118 butts (below, be called the 2nd position).
The 2nd position be equivalent to be arranged on the slider 101 relief cam 107 not with the non-butt position of the arm 56A butt of exhaust valve rocker arm 56.Thereby, after the engine start, and though motor 10 carry out in compression stroke α, combustion stroke, exhaust stroke and the intake stroke any one, shown in Fig. 8 (b), exhaust valve rocker arm 56 all can with exhaust cam 46 butts, thereby along with the cam profile of exhaust cam 46 opens and closes exhaust valve 36.
Therefore, by this mechanism of decompressor 200 also can be only when the engine start, in the compression stroke α of motor 10, open exhaust valve 36, thus the compression pressure when lowering engine start.Thereby, adopt in the engine start mode under the situation of accumulator drive mode, compare with the situation that the mechanism of decompressor is not set, can adopt small-sized starting motor; In addition, under the situation that adopts the Kick-start mode, can reduce the needed recoil force of engine start, make engine start easily.
In the present embodiment, the above-mentioned mechanism of decompressor 200 has centrifugal governor 100, between the peripheral part of the interior perimembranous of the slider 101 of this centrifugal governor 100 and camshaft 50, dispose force application part 115 to this slider 101 application of forces, so, with the 1st mode of execution similarly, the cam shaft that can shorten the mechanism of decompressor 200 to total length.
In addition, in this structure because slider 101 is provided with relief cam 107 integratedly, thus can reduce the number of parts, can also shorten thus cam shaft to total length.In addition, owing to do not need to be provided with the engagement formation that makes slider and relief cam engagement, so, the complicated of component shape can be avoided, thereby the simplification of the mechanism of decompressor can be realized.
Further, also be to run through between the slider 101 and counterweight maintenance body 103 that is inserted on the camshaft 50 in this formation owing to governor weight 82 is maintained at, so, with the 1st mode of execution similarly, do not need axle to support the parts of governor weight, thereby can realize that the component number purpose further reduces and the simplification of mechanism, and owing to do not need governor weight is configured in the outside on every side of relief cam, so can realize reducing of mechanism of decompressor diameter.
Therefore, the mechanism of decompressor 70 of this structure also can be realized the miniaturization and the light of all shapes, can realize the attenuating of motor 10 rotary loads, the miniaturization of cylinder head 13 and the light around the cylinder head 13.
And, in the mechanism of decompressor 200 of this structure, during engine start, slider 101 moves to exhaust cam 46 sides (above-mentioned the 1st position), after the engine start, slider 101 moves to an opposite side (above-mentioned the 2nd position) of exhaust cam 46, so, even for example do not use the rocking arm of DOHC motor etc., but intake cam and the directly downward motor that pushes each of exhaust cam by being configured in intake valve and exhaust valve top, after engine start, slider 101 is evaded in the position standby of leaving exhaust cam.Thereby this mechanism of decompressor 200 can also be applied to directly push with exhaust cam the motor of exhaust valve downwards.
More than based on a mode of execution the present invention has been described, still, be appreciated that the present invention is not limited to this.For example, in the above-described embodiment, adopt helical spring situation, still, also can adopt helical spring force application part in addition although understand the force application part 95,115 that is configured in slider 81,101 inboards.
In addition, in the present embodiment, though illustration apply the present invention to situation in the mechanism of decompressor of automatic two-wheel vehicle used single cylinder engine, but, also can be applied to have in the mechanism of decompressor of motor of multi cylinder, in addition, also be not limited to automotive bicycle, can also be widely used in the mechanism of decompressor of motor of three-wheeled vehicle with ATV (full landform traveling vehicle) classification, four-wheel car or the like various vehicles.
Claims (5)
1. a mechanism of decompressor is characterized in that, the described mechanism of decompressor comprises:
Centrifugal governor, described centrifugal governor is arranged on the camshaft of motor, and has by the centrifugal force of governor weight along the axially movable slider of this camshaft;
Relief cam, the slider of described relief cam and this centrifugal governor is provided with integratedly; And
Force application part, described force application part are arranged between the interior perimembranous of the peripheral part of described camshaft and described slider, and overcome described centrifugal force with the direction that stops described slider and move on to the described slider application of force,
Wherein, described force application part is by described slider and described camshaft clamping.
2. the mechanism of decompressor according to claim 1 is characterized in that, described camshaft is provided with outstanding mobile prevention parts to stop described slider to move at the circumferencial direction of camshaft.
3. the mechanism of decompressor according to claim 1 and 2 is characterized in that, described slider has integratedly and runs through the tube portion that is inserted on the camshaft periphery and extend the lip part that is provided with and described governor weight is led at the peripheral part of this one,
Described force application part is configured in the interior week of described tube portion.
4. the mechanism of decompressor according to claim 1 and 2 is characterized in that, will be arranged on the exhaust valve rocker arm with the arm of described relief cam butt.
5. the mechanism of decompressor according to claim 3 is characterized in that, is arranged on the exhaust valve rocker arm with the arm of described relief cam butt.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005343787 | 2005-11-29 | ||
| JP2005343787 | 2005-11-29 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1975118A CN1975118A (en) | 2007-06-06 |
| CN100532793C true CN100532793C (en) | 2009-08-26 |
Family
ID=38125413
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2006101427175A Expired - Fee Related CN100532793C (en) | 2005-11-29 | 2006-10-30 | Decompression mechanism |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN100532793C (en) |
| ES (1) | ES2320507B1 (en) |
| TW (1) | TW200724778A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| TWI451031B (en) * | 2010-05-12 | 2014-09-01 | Sanyang Industry Co Ltd | Engine decompression mechanism |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2746985B2 (en) * | 1989-02-21 | 1998-05-06 | 本田技研工業株式会社 | Engine camshaft device |
| CN2550508Y (en) * | 2002-04-28 | 2003-05-14 | 重庆宗申技术开发研究有限公司 | Pressure reducing structure for engine start |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01118112U (en) * | 1988-02-03 | 1989-08-09 | ||
| JPH06280530A (en) * | 1993-03-24 | 1994-10-04 | Suzuki Motor Corp | Decompressor device for internal combustion engine |
| JPH0734834A (en) * | 1993-07-14 | 1995-02-03 | Mitsubishi Heavy Ind Ltd | Decompressing device of engine |
| DE19611031C2 (en) * | 1996-03-20 | 1999-04-15 | Kwang Yang Motor Co | Decompression device for the automatic speed-dependent reduction of the gas pressure in the combustion chamber of a valve-controlled internal combustion engine |
-
2006
- 2006-10-30 CN CNB2006101427175A patent/CN100532793C/en not_active Expired - Fee Related
- 2006-11-01 TW TW095140351A patent/TW200724778A/en not_active IP Right Cessation
- 2006-11-03 ES ES200602792A patent/ES2320507B1/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2746985B2 (en) * | 1989-02-21 | 1998-05-06 | 本田技研工業株式会社 | Engine camshaft device |
| CN2550508Y (en) * | 2002-04-28 | 2003-05-14 | 重庆宗申技术开发研究有限公司 | Pressure reducing structure for engine start |
Also Published As
| Publication number | Publication date |
|---|---|
| ES2320507A1 (en) | 2009-05-22 |
| TW200724778A (en) | 2007-07-01 |
| CN1975118A (en) | 2007-06-06 |
| ES2320507B1 (en) | 2010-01-12 |
| TWI323308B (en) | 2010-04-11 |
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