CN1268631A - Compensation of inertia forces device for vehicle engine - Google Patents
Compensation of inertia forces device for vehicle engine Download PDFInfo
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- CN1268631A CN1268631A CN 00105320 CN00105320A CN1268631A CN 1268631 A CN1268631 A CN 1268631A CN 00105320 CN00105320 CN 00105320 CN 00105320 A CN00105320 A CN 00105320A CN 1268631 A CN1268631 A CN 1268631A
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- One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
Abstract
The invention is to reduce stirring resistance to the utmost, reduce deterioration of oil to the utmost, and arrange a balance weight by avoiding partition and formation of a special chamber in a crank case in an engine for a vehicle having a start clutch stored in the crank case. A start clutch includes a disc-like clutch plate rotated in synchronization with the rotation of a crankshaft while the movement along the axis parallel to the crankshaft is inhibited, a friction plate disposed opposite to the clutch plate, a ramp plate for pressing the friction plate to be in the frictional engagement with the clutch plate according to the increase in rotating speed of the clutch plate, and a clutch outer engaged with the friction plate to cover the ramp plate. A balance weight is provided in a portion of the ramp plate that is covered with the clutch outer.
Description
The present invention relates to a kind of starting clutch is accommodated in being used in the mobile engine in the crankcase and regulates the improvement of Equilibrator of the amount of unbalance of bent axle; This starting clutch can be transmitted to the rotating power of bent axle on the driving wheel.
The Equilibrator of the mobile engine of prior art is for example known by real fair 2-40343 communique etc.
In above-mentioned prior art, owing to its stirs the deterioration that the oil that retains in the crank box is subjected to stirring resistance and produces oil, and the crankshaft room that counterweight is housed in and takes in bent axle divides to turn up the soil and is located in the special-purpose cell of crankcase chamber for fear of the counterweight of synchronously rotating around the axis parallel with bent axle and this bent axle.Therefore, the structure in the crankcase complicates, and crankcase is maximized.
The present invention makes in view of above-mentioned situation, its objective is provide a kind of can do one's utmost to reduce to stir resistance and do one's utmost to reduce oil deterioration, can avoid in crankcase dividing the Equilibrator that forms in the mobile engine that special-purpose ground, chamber disposes counterweight.
To achieve these goals, the present invention is characterized in that starting clutch has: discoideus clutch plate in the starting clutch that the rotating power of bent axle can be passed to driving wheel is accommodated in mobile engine in the crankcase; Friction plate; Swash plate; Clutch outer member.Above-mentioned clutch plate the time along mobile being prevented from of the axis parallel with bent axle, with the rotation of above-mentioned bent axle synchronously around above-mentioned axis rotation; Above-mentioned friction plate and above-mentioned clutch plate relatively are configured; Above-mentioned swash plate can be according to the increase of the rotating speed of above-mentioned clutch plate along pushing above-mentioned friction plate with the direction of above-mentioned friction plate frictional engagement on above-mentioned clutch plate, this swash plate be arranged at and above-mentioned clutch plate between clip the position of above-mentioned friction plate; Above-mentioned clutch outer member forms the cup-shaped that covers above-mentioned swash plate, and meshes with above-mentioned friction plate; On the part that the above-mentioned clutch outer member of the usefulness of above-mentioned swash plate is covered with, be provided with the counterweight of the amount of unbalance that is used to regulate bent axle.
According to such formation, counterweight is located at by clutch plate, friction plate and clutch outer member and is covered with on the swash plate of global shape, the oil that is stored in the crank box is restricted to minute quantity in the circulation of the interior outer room of starting clutch, therefore, can avoid the stirring of the oil that counterweight produces with doing one's utmost.Therefore, when can reduce to stir resistance with doing one's utmost, do one's utmost to reduce the deterioration of oil, form dedicated chamber ground and dispose counterweight but also can avoid in crankcase dividing, can not cause the complicate maximization of float chamber of structure in the crank box owing to the configuration of counterweight.
Fig. 1 is the side view of the bicycle of band auxiliary engine.
Fig. 2 is the longitudinal section of motor, is the 2-2 line sectional view of Fig. 3.
Fig. 3 is the 3-3 line sectional view of Fig. 2.
Fig. 4 is the 4-4 line sectional view of Fig. 2.
Fig. 5 is the amplification view of starting clutch.
Fig. 6 is the front view of the swash plate of seeing from the 6-6 line direction of arrow of Fig. 5.
Below the one embodiment of the invention shown in reference to the accompanying drawings illustrate example of the present invention.
Fig. 1～Fig. 6 is the figure of expression one embodiment of the invention.Fig. 1 is the side view that has the bicycle of auxiliary engine; Fig. 2 is the longitudinal section of motor, is the sectional view of the 2-2 line of Fig. 3; Fig. 3 is the 3-3 line sectional view of Fig. 2; Fig. 4 is the 4-4 line sectional view of Fig. 2; Fig. 5 is the amplification view of starting clutch.
At first, as shown in Figure 1, the car body framework 10 of the bicycle that has auxiliary engine of dilly have the head pipe 11 of its front end, from the beginning manage the 11 decline frameworks 12 that extend to the rear lower side, manage 11 seat post 13 parallel and that extend upward from the upper rear end of decline framework 12 with head.Head pipe 11, decline framework 12 and seat post 13 are formed as one by castings such as aluminum alloys.And decline framework 12 forms the open roughly U word shape in below.
But on head pipe 11, supporting to steering front fork 14, axle is supporting front-wheel W in the lower end of this front fork 14
F, be provided with the handle 15 of steering in the upper end of front fork 14.In addition, at the rear vehicle fork 16 of the pairing left and right of rearward extending from the rear end of decline framework 12 ... the rear end between supporting trailing wheel W as driving wheel
R, between the rear end of the above-below direction intermediate portion of seat post 13 and two rear vehicle forks 16, be provided with left and right a pair of support 17.
Taking in fuel tank 21 in the first half of decline framework 12, the lid 22 that is provided with on the upper end of this fuel tank 21 is being given prominence to upward from decline framework 12.
Freely supporting pedal axle 23 in the revolution of the rear portion of decline framework 12, fixing at the two ends of this pedal axle 23 for being sitting in the pedal 24 that the driver on the saddle steps ..., this pedal 24 ... be configured in the both sides of decline framework 12.And under the state in the bicycle walking direction the place ahead that has auxiliary engine, the driving sprocket wheel 25 in that the right side and the pedal axle 23 of decline framework 12 disposing coaxially is being located at trailing wheel W coaxially
ROn by on movable sprocket 26 and the above-mentioned driving sprocket wheel 25 around the chain 27 of hanging ring-type.
With reference to Fig. 2～4, the axis of the cylinder bore 31 that the cylinder block 30 of motor 28 is had its cylinder block 30 essentially horizontally is being configured along the fore-and-aft direction of bicycle, is configured in the cylinder head in the place ahead of this cylinder block 30 and the crankcase 33 that is configured in the rear of cylinder block 30 and is combined on the cylinder block 30.Be embedded in the cylinder bore 31 that is located on the cylinder block 30 piston 34 free slidings, connecting bent axle 36 by connecting rod 35 on this piston 34, this bent axle 36 has along the axis of bicycle width direction.The crankcase 33 of accommodating this bent axle 36 is that the direct joint ground by the countercylinder body 30 of avoiding upper box body 38 mutually combines lower part box 37 and upper box body 38 and forms, this lower part box 37 combines with cylinder block 30, above-mentioned upper box body 38 forms at the rear portion of decline framework 12, and the parting plane 39 of lower part box 37 and upper box body 38 parallels with the axis of the axis of cylinder bore 31 and bent axle 36.
Bent axle 36 is accommodated in lower part box 37 1 sides in the two tanks 37,38 that constitutes crankcase 33.The two mutual positions that crankpin 36a is clipped in of this bent axle 36 freely are being supported in the revolution of lower part box 37 1 sides.That is, bent axle 36 has integratedly: crank pin 36a; Crank arm 36b, the 36c of crankpin 36a both sides; Crank journal 36d, 36e.This crank pin 36a is connecting connecting rod 35, and above-mentioned crank journal 36d, 36e are giving prominence to foreign side from two crankweb 36b, 36c.Two crank journal 36d, 36e freely are bearing on the bearing 40,41 by ball bearing 42,43 rotations, and this bearing 40,41 is fixed on the lower part box 37.
Above-mentioned two bearings 40,41 are clipped between cylinder block 30 and the lower part box 37 and are being configured.By be configured in cylinder bore 31 around and screw in 4 stud bolts 44,44 in the lower box 37 ... be threaded over each stud bolt 44,44 respectively ... on nut 45,45 cylinder head 32, cylinder block 30, bearing 40,41 and lower part box 37 are tightened to together.That is, plant stud bolt 44,44 on lower part box 37 by screwing in an end ... pass bearing 40,41, cylinder block 30 and cylinder head 32 respectively, from the outstanding stud bolt 44,44 of cylinder head 32 ... the other end on screw thread in conjunction with nut 45,45 ...In addition, from each stud bolt 44,44 ... and nut 45,45 ... the position that formed fixed position is left, cylinder head 32 by 1 or a plurality of bolt 46 be fixed on the cylinder block 30.
Foreign side's side that the attitude with towards fore-and-aft direction the place ahead of bicycle in two bearings 40,41 is configured in the bearing 40 in left side is disposing generator 48, and the rotor 49 of this generator 48 is fixed on from an end of the outstanding bent axle 36 of bearing 40.The stator 50 of above-mentioned generator 48 is fixed on the 40a of carrying cylinder portion that is darted at integratedly on the bearing 40, and coaxially round an end of this bent axle 36.
Forming firing chamber 54 between cylinder block 30 and the cylinder head 32, this firing chamber 54 is faced with the part at the top of piston 34, and with towards the posture in fore-and-aft direction the place ahead of bicycle with center configuration from the journal offset of cylinder bore 31 to the position on right side.
In addition, ignition spark plug 57 is installed on cylinder head 32, the inner of this ignition spark plug 57 is faced with firing chamber 54.
Be provided with the intakeport 55 that can be connected with above-mentioned firing chamber 54 on the top of cylinder block 30.Be provided with the relief opening 56 that can communicate with above-mentioned firing chamber 54 in the bottom of cylinder block 30.
Aspirating valves 58 and outlet valve 59 are configured in the top of the cylinder bore 31 in the cylinder block 30 that is located at engine body 29, this Aspirating valves 58 is used to switch the connection blocking of 54 of intakeport 55 and firing chambers, and this outlet valve 59 is used to switch the blocking that is communicated with of relief opening 56 and 54 of firing chambers.This Aspirating valves 58 and outlet valve 59 can be along carrying out on-off action with the direction of the parallel axes of cylinder bore and being supported on the cylinder block 30 and by to closing the pushing of valve direction elasticity.
These Aspirating valvess 58 and outlet valve 59 passive valve mechanisms 60 driven for opening and closing.This active valve mechanism 60 have timing actuation gear 61, with timing driven gear 63, cam 64, suction side rocking arm 65, the exhaust side rocking arm 66 of above-mentioned timing actuation gear engagement.Above-mentioned timing actuation gear 61 is fixed on the bent axle 36, fulcrum 62 rotations that above-mentioned timing driven gear 63 usefulness are fixed on the cylinder block 30 are freely being supported, above-mentioned cam 64 is formed on the timing driven gear 63, above-mentioned suction side rocking arm 65 is driven in above-mentioned cam 64 ground and shakes, and be supported on the cylinder block 30 and with above-mentioned Aspirating valves 58 interlocks, be connected; Above-mentioned exhaust side rocking arm 66 is driven in above-mentioned cam 64 ground and shakes, be supported on the cylinder block 30 and with above-mentioned outlet valve 59 interlocks, be connected.
Foreign side's side that the posture with fore-and-aft direction the place ahead of bicycle of above-mentioned timing actuation gear 61 in above-mentioned two bearings 40,41 is configured in the bearing 41 on right side is arranged on the other end of bent axle 36.This timing actuation gear 61 is that 1/2 ground passes to timing driven gear 63 and cam 64 with the rotating power deceleration of bent axle 36, that is, 1/2 ground that cam 64 is decelerated to the rotational speed of bent axle 36 is rotated.
Connecting the downstream of the sucking pipe 72 that communicates with intakeport 55 on the top of cylinder block 30, the upstream extremity of this sucking pipe 72 is connected with the downstream of vaporizer 73.This vaporizer 73 is being configured in its part of rear side of fuel tank 21 is accommodated in the decline framework 12 of car body framework 10.
The upstream extremity that is connecting the outlet pipe 76 that communicates with exhaust 56 in the bottom of cylinder block 30.The below of this outlet pipe 74 by motor 28 extend to the rear and be configured in motor 28 and trailing wheel W
RBetween exhaust silencer 75 (with reference to Fig. 1) be connected.
In Fig. 2, the two ends that main shaft 94 is freely being supported in revolution on the lower box 37 in crankcase 33, this main shaft 94 has the axis parallel with bent axle 36.End with pedal axle 23 of the axis parallel with main shaft 94 freely be bearing in by ball bearing 95 rotations in the upper box body 38 of crankcase 33 along on the left side sidewall of the fore-and-aft direction of bicycle.In above-mentioned upper box body 38 along freely supporting the outer distolateral of revolving drum axle 96 by ball bearing 97 rotation on the right sidewall of bicycle fore-and-aft direction, this revolving drum axle 96 is distolateral round another of pedal axle 23 coaxially, the inner end of revolving drum axle 96 is freely being supported by pedal axle 23 relative rotations, is clamping roller bearing 98 between the outer distolateral and pedal axle 23 of revolving drum axle 96.That is, coaxial pedal axle 23 and revolving drum axle 96 can be bearing on the upper box body 38 of crankcase 33 with the relative rotation, are fixing driving sprocket wheel 25 in the outer end of revolving drum axle 96.
Fixedly mounting elementary actuation gear 99 on the side 36c of a pair of crank arm 36b, 36c that bent axle 36 is possessed, the elementary driven gear 100 that is meshed with this elementary actuation gear 99 can be supported on the main shaft 94 with the relative rotation.
With reference to Fig. 5, starting clutch 85 is installed on main shaft 94.This starting clutch 85 has discoideus clutch plate 86, friction plate 87, swash plate 88, clutch outer member 89; This clutch plate 86 time along mobile being prevented from of the direction of the axis of main shaft 94 with axis parallel with bent axle 36, around the axis rotation of this main shaft 94; Above-mentioned friction plate 87 and above-mentioned clutch plate 86 relative configurations; Above-mentioned swash plate 88 can be according to the increase of the rotating speed of clutch plate 86 and friction plate 87 is pushed to the direction with clutch plate 86 frictional engagement, and be configured in and above-mentioned clutch plate 86 between clip on the position of above-mentioned friction plate 87; Above-mentioned clutch outer member 89 forms the cup-shaped of the above-mentioned swash plate 88 of covering and meshes with above-mentioned friction plate 87.
Be axially located the ground spline in conjunction with wheel hub 90 cylindraceous on main shaft 94, and elementary driven gear 100 relative rotations freely are supported on the wheel hub 90.The interior Zhou Huajian of clutch plate 86 is combined on the periphery of wheel hub 90, and elementary driven gear 100 is connected on the clutch plate 86 by shock absorber 101.
Axial direction can connect slidably spline in conjunction with swash plate 88 on above-mentioned wheel hub 90, is provided with spring 91 between clutch plate 86 and swash plate 88, and this spring 91 produces the power that above-mentioned both intervals between 86,88 are enlarged.
With reference to Fig. 6, on swash plate 88 and faces above-mentioned clutch plate 86 opposition sides, be provided with accepting groove 102,102 ..., this accepting groove 102,102 ... accommodate roller 92 emphatically respectively ..., and can make the radial rolling of these heavy rollers 92 along main shaft 94.With opposite side and each heavy roller 92 of swash plate 88 ... the backboard 93 that connects is installed on the wheel hub 90.And, at each accepting groove 102,102 of the radial direction that carries over main shaft 94 ... the outer distolateral inclined-plane 102a that forming ..., this inclined-plane 102a ... move closer to backboard 93 along with going toward the outer side.
Clutch 89 forms and covers swash plate 88, each heavy roller 92 ... and the cup-shaped of backboard 93, and can be bearing on the main shaft 94 with rotating relatively freely.Meshing the periphery of friction plate 87 on the opening end of this clutch outer member 89, output gear 104 is fixedly mounted on the clutch outer member 89.
In this starting clutch 85, the rotational speed of driven clutch plate 86 becomes specified value when above by elementary actuation gear 99, elementary driven gear 100 and shock absorber 101 from bent axle 36, corresponding therewith, each heavy roller 92 ... owing to action of centrifugal force is climbed and is stepped on inclined-plane 102a ... thereby swash plate 88 pushes friction plate 87 towards the direction with clutch plate 86 frictional engagement, thus, clutch plate 86 is connected with clutch outer member 89 by friction plate 87, and the rotating power of the bent axle 36 of direction of advance passes to output gear 104.
And in the swash plate 88 of starting clutch 86, on the part that is covered with by clutch outer member 89, for example be provided with counterweight 103 integratedly on the roughly half cycle at the peripheral part of swash plate 88, this counterweight 103 is used to regulate the amount of unbalance of bent axle 36.
The output gear 104 of above-mentioned starting clutch 85 is connected with revolving drum axle 96 by the 1st planetary gear type speed reducer 105.The bearing 106 of the 1st planet gear type speed reducer 105 can not be installed on the revolving drum axle 96 with the relative rotation, sun gear 107 and output gear 104 engagements, and gear ring 108 stops the axis of wraparound rotating drum shaft 96 to be incorporated into rotatably on the main shaft 94.
The 2nd planetary gear type speed reducer 111 relative with the 1st planetary gear type speed reducer 105 in the position that isolates some intervals is installed on the pedal axle 23, the bearing 112 of the 2nd planetary gear type speed reducer 111 is not combined on the upper box body 38 rotatably around the axis of pedal axle 23, gear ring 113 can be bearing on the pedal axle 23 rotatably around axis, and sun gear 114 can supported by gear ring 113 rotatably around axis.
105,111 of the 1st and the 2nd planetary gear type speed reducers, on pedal axle 23, the shifter 115 coaxial with this pedal axle 23 is installed by helical gear, frictional engagement spring 116 on the periphery of this shifter 115, and this spring 116 stops the axis rotation of shifter 115 around pedal axle 23 by combining with upper box body 38.And, when pedal axle 23 rotates along the direction of advance of bicycle, owing to being in the shifter 115 that rotates the state that is prevented from, the frictional engagement with spring 116 moves to the 1st planetary gear type speed reducer 105 sides, in addition, at pedal shaft 23 during, because the frictional engagement with spring 116 is in and rotates the state shifter 115 that is prevented from and move to the 2nd planetary gear type speed reducer 111 sides along the laggard direction rotation of bicycle.Shifter 115 ratchet-types are combined on the bearing 106 of the 1st planetary gear type speed reducer 105, thus, can carry out transmission of power to bearing 106 from shifter 115, but can not carry out transmission of power to shifter 115 from bearing 106; And shifter 115 can be combined on the gear ring 113 of the 2nd planetary gear type speed reducer 111 by ratchet-type, thus, and can be from shifter 115 to gear ring 113 transferring power, but can not be from gear ring 113 to shifter 115 transferring power.
Therefore, by pedal 24 ... step and with pedal axle 23 when the rotation of the direction of advance of bicycle drives, shifter 115 moves to the position that combines with bearing 106 ratchet-types of the 1st planetary gear type speed reducer 105, by putting on the pedal axle 23, can by shifter 115 and bearing 106 rotating power be delivered on the revolving drum axle 96 from pedal axle 23 greater than the rotating power that acts on the rotation resistance on the shifter 115 owing to frictional engagement with spring 116.
On the other hand, the helical gear 117 that is meshed with the periphery of sun gear 114 in the 2nd planetary gear type speed reducer 111 is freely being supported in rotation on main shaft 94, frictional engagement spring 118 on this oblique wheel 117, and this spring 118 is because of stoping the axis rotation of helical gear 117 around main shaft 94 with combining of lower part box 37.And, on main shaft 94, rotating member 119 can not be installed with the relative rotation, these rotating member 119 compartment of terrains are relative with above-mentioned helical gear 117.
By treadling 24 ... when the laggard direction rotation of bicycle drove, shifter 115 moved, up to combining with gear ring 113 ratchet-types of the 2nd planetary gear type speed reducer 111 with pedal axle 23.By being applied on the pedal axle 23 greater than the rotating power that acts on the rotation resistance on the shifter 115 because of frictional engagement with spring 116, rotating power is delivered on the helical gear 117 by shifter and the 2nd planetary gear type speed reducer 111 from pedal axle 23, the helical gear 117 that is in the state that rotation has been prevented from owing to the frictional engagement with spring 118 moves to rotating member 119 sides thus.Helical gear 117 ratchet-types are combined on the rotating member 119, so that can be to rotating member 119 transferring power from this helical gear 117 and can not be from rotating member 119 to helical gear 117 transferring power.
Therefore, drive pedal shaft 23 by laggard direction rotation along bicycle, make helical gear 117 move, up to combining with rotating member 119, by putting on the pedal axle 23, can by shifter the 115, the 2nd planetary gear type speed reducer 111, helical gear 117 and rotating member 119 rotating power be transmitted on the main shaft 94 from pedal axle 23 greater than the rotating power that acts on the rotation resistance on the helical gear 117 because of frictional engagement with spring 118.Because the rotating power of main shaft 94 is delivered on the bent axle 36 by clutch plate 86, shock absorber 101, elementary driven gear 110 and the elementary actuation gear 99 of starting clutch 85, motor 28 is started.
Like this, according to the rotation of the direction of advance of pedal axle 23 and the rotation of laggard direction, connect shifter 115 selectively, the rotating power of the direction of advance of pedal axle 23 is passed to the 1st planetary gear type speed reducer 105 of revolving drum axle 96, the rotating power of the laggard direction of pedal axle 23 is passed to the 2nd planetary gear type speed reducer 111 of helical gear 117, by power being delivered to main shaft 94 from helical gear 117, can realize the starting of the motor 28 that undertaken by the rotary manipulation of the laggard direction of pedal axle 23 with the simple structure that does not use complicated overrunning clutch from the transmission of power of the 2nd planetary gear type 111.
As Fig. 2, shown in Figure 3, the lower ending opening portion towards decline framework 12 of seat post 13 by vent cap 77 blockings with breathing pipe 76, and this vent cap 77 is clamped in upper box body 38 and is fixed between the pressing plate 78 on this upper box body 38.In addition, between vent cap 77 and pressing plate 78, forming mazy type road 79, these mazy type road 79 one ends and 33 interior connections of crankcase, its other end is communicated with above-mentioned breathing pipe 76.The breathing pipe gas that in crankcase, produces (Block リ-ザ ガ ス) on one side during by above-mentioned mazy type road 79 on one side the separating oil composition flow to breathing pipe 76 sides.Above-mentioned breathing pipe 76 is connected with air-strainer (not shown) in being configured in decline framework 12, is sneaking into above-mentioned breathing pipe gas from this sky filter cleaner in vaporizer 73 sucks air-breathing the motors 28.
Below this embodiment's effect is described, the crankcase 33 of motor 28 forms by being mutually combined by lower part box of cutting apart with the parting plane 39 of the parallel axes of bent axle 36 37 and upper box body 38.Because only in conjunction with lower part box 37, the seal construction of the junction plane of cylinder block 30 and crankcase 33 is simple, thereby can improve sealing on cylinder block 30.
In addition, in bent axle 36, be rotated freely in lower box 37 sides and supporting because crankpin 36a is clipped in 2 mutual positions, so, the supporting rigidity of bent axle 36 can be improved.Help to improve the durability of bent axle 36.
Because the parallel axes of the cylinder bore 31 in above-mentioned parting plane 39 and the cylinder block 30, lower part box 37 constitute the open bowl shape in top, can make the shape simplification of lower part box 37.
Have again, because bent axle 36 is bearing in the bearing 40,41 that is fixed on the lower part box 37 by ball bearing 42,43 respectively, so, can avoid the increase of machining period number, and can precision support crankshaft 36 well.In the structure in the bearing hole between a pair of member that bent axle 36 usefulness bearings supportings and this Bearing Installation is being formed on the both sides that are configured in bent axle 36, must under the assembled state of the structure of aforementioned both sides, implement to process the supporting precision of guaranteeing bent axle 36 in the above-mentioned bearing hole, but by making ball bearing 42,43 is installed in structure on each bearing 40,41 respectively, does not need to implement above-mentioned the time processing and can support bent axle 36 accurately.
And, be provided with the counterweight 103 of the amount of unbalance that is used to regulate bent axle 36 on the part that covers by clutch 89 of the swash plate 88 in starting clutch 85, be restricted to minute quantity owing to be stored in the circulation at the interior outer room of starting clutch 85 of oil in the crankcase 33, so can do one's utmost to avoid the stirring of the oil that brought by counterweight 103.Therefore, can do one's utmost to reduce to stir impedance and can do one's utmost to reduce oily deterioration.Configuration counterweight 103 be can avoid in crankcase 33, dividing with forming special-purpose chamber, the complex structure in the crankcase 33, the maximization of float chamber 33 can not caused owing to the configuration of counterweight 103.
More than, understand embodiments of the invention in detail, but the present invention is not limited to the foregoing description, can not break away from the present invention ground that is recorded in the Patent right requirement and carry out all design alterations.
If adopt above-mentioned the present invention, can reduce to stir impedance with doing one's utmost, and can avoid in crankcase, dividing, form special-purpose ground, chamber configuration counterweight, can not cause the maximization of the complex structure float chamber in the crankcase owing to the configuration of counterweight.
Claims (1)
1. the Equilibrator in the mobile engine in this mobile engine, can pass to driving wheel (W with the rotating power of bent axle (36)
R) starting clutch (85) be accommodated in the crankcase (33), it is characterized in that starting clutch (85) has discoideus clutch plate (86), friction plate (87), swash plate (88), clutch outer member (89); Above-mentioned clutch plate (86) time along mobile being prevented from of the direction of the axis parallel with bent axle (36), with above-mentioned bent axle (36) synchronously around above-mentioned axis rotation; Above-mentioned friction plate (87) relatively disposes with above-mentioned clutch plate (86); Above-mentioned swash plate (88) can push above-mentioned friction plate (87) along the direction with above-mentioned clutch plate (86) frictional engagement according to the increase of the rotating speed of above-mentioned clutch plate (86), and is configured between itself and the above-mentioned clutch plate (86) and clips on the position of above-mentioned friction plate (87); Above-mentioned clutch outer member (89) forms the cup-shaped of the above-mentioned swash plate of covering (88) and meshes with above-mentioned friction plate (87); On the part that is covered with by above-mentioned clutch outer member (89) of above-mentioned swash plate (88), be provided with the counterweight (103) of the amount of unbalance that is used to regulate bent axle (36).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP092656/1999 | 1999-03-31 | ||
| JP11092656A JP2000283239A (en) | 1999-03-31 | 1999-03-31 | Balancer device in engine for vehicle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1268631A true CN1268631A (en) | 2000-10-04 |
| CN1143968C CN1143968C (en) | 2004-03-31 |
Family
ID=14060524
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB001053205A Expired - Fee Related CN1143968C (en) | 1999-03-31 | 2000-03-31 | Compensation of inertia forces device for vehicle engine |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP2000283239A (en) |
| CN (1) | CN1143968C (en) |
| ID (1) | ID25433A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100441903C (en) * | 2003-09-26 | 2008-12-10 | 本田技研工业株式会社 | Balancer driven gear of engine |
| CN100458211C (en) * | 2005-05-10 | 2009-02-04 | 福特环球技术公司 | Inertial torque reaction management with selectively engageable counter rotating component |
| CN102135157A (en) * | 2011-01-27 | 2011-07-27 | 李云合 | Clutch gear applied on gearbox input shaft of motorcycle |
| CN102927198A (en) * | 2011-08-08 | 2013-02-13 | 福特环球技术公司 | Internal combustion engine with mass balancing and method for operating such an internal combustion engine |
| CN108482096A (en) * | 2018-04-18 | 2018-09-04 | 王青林 | A kind of cluster engine with adaptive equalization component |
-
1999
- 1999-03-31 JP JP11092656A patent/JP2000283239A/en active Pending
-
2000
- 2000-03-31 CN CNB001053205A patent/CN1143968C/en not_active Expired - Fee Related
- 2000-03-31 ID IDP20000260A patent/ID25433A/en unknown
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100441903C (en) * | 2003-09-26 | 2008-12-10 | 本田技研工业株式会社 | Balancer driven gear of engine |
| CN100458211C (en) * | 2005-05-10 | 2009-02-04 | 福特环球技术公司 | Inertial torque reaction management with selectively engageable counter rotating component |
| CN102135157A (en) * | 2011-01-27 | 2011-07-27 | 李云合 | Clutch gear applied on gearbox input shaft of motorcycle |
| CN102927198A (en) * | 2011-08-08 | 2013-02-13 | 福特环球技术公司 | Internal combustion engine with mass balancing and method for operating such an internal combustion engine |
| CN102927198B (en) * | 2011-08-08 | 2016-04-27 | 福特环球技术公司 | There is the internal-combustion engine of mass balance and the method for operating this internal-combustion engine |
| CN108482096A (en) * | 2018-04-18 | 2018-09-04 | 王青林 | A kind of cluster engine with adaptive equalization component |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1143968C (en) | 2004-03-31 |
| ID25433A (en) | 2000-10-05 |
| JP2000283239A (en) | 2000-10-13 |
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