CN1615397A - Engine - Google Patents

Abstract

An engine capable of transmitting a rotational force between a crankshaft and first and second driven shafts through first and second drive gears on the crankshaft side and first and second driven gears on the first and second driven shaft sides, wherein the first drive gear is fixedly installed on the crankshaft, the second drive gear is detachably engaged with the first drive gear so as to be overlapped with the engaged part of the first drive gear, the transmission of the rotational force between the crankshaft and the first driven shaft is performed directly between the first drive gear and the first driven gear, and the transmission of the rotational force between the crankshaft and the second driven shaft is performed through the second drive gear between the first drive gear and the second driven gear.

Description

Motor

Technical field

The present invention relates to a kind of motor, first actuation gear, second actuation gear that this motor utilization is installed on the crankshaft rotate driving first driven shaft, second driven shaft respectively, for example lubricant oil pump shaft, balace weight axle, perhaps, for example utilize the foot pedal starting beam warp to drive crankshaft by above-mentioned first actuation gear rotation.

Background technique

For example, in the motor vehicular engine, usually, utilize a plurality of actuation gears that are installed on the crankshaft respectively, for example rotation drives lubricating pump, balace weight axle (for example, with reference to Japanese patent laid-open 8-189323 communique).In this case, above-mentioned each actuation gear is set to the external diameter corresponding with the purpose that is driven parts.For example, because with speed driving lubricating pump, in addition with the rotational speed driven equilibrium device axle identical with the rotation of motor with the rotational delay of motor, so, usually, set the lubricating pump driving for minor diameter with gear, the balace weight axle is driven set major diameter for gear.In addition, on above-mentioned crankshaft, with above-mentioned a plurality of actuation gears together, crankshaft parts such as generator, cam sprocket wheel are installed, be necessary these gears or crankshaft parts with compact as far as possible and transferring power and mode are for ease of maintenaince loaded reliably.

But, when only being configured in above-mentioned a plurality of actuation gears on the crankshaft side by side, in order securely actuation gear to be installed on the crankshaft, the thickness thickening of the axial direction of each actuation gear must be existed the elongated problem of crank axial length thus.In addition, by being pressed under the situation that above-mentioned actuation gear is installed, the maintenance of also worrying the replacing etc. of these actuation gears problem of difficulty that becomes.

Summary of the invention

The present invention its objective is in view of above-mentioned existing truth forms, and provides a kind of length of crankshaft of can avoiding elongated, and maintenance such as the replacing of actuation gear is easy to motor in addition.

Technological scheme 1 described invention, crankshaft and first, between second driven shaft, first actuation gear via above-mentioned crankshaft side, second actuation gear and above-mentioned first, first driven gear of the second driven shaft side, second driven gear transmits the motor of rotating force, it is characterized in that, when being fixedly secured to above-mentioned first actuation gear on the above-mentioned crankshaft, with above-mentioned second actuation gear in the mode on the portion of the being engaged part that overlaps onto this first actuation gear, and be coupled to removably on this first actuation gear, transmission for the rotating force between above-mentioned crankshaft and above-mentioned first driven shaft, be between above-mentioned first actuation gear and above-mentioned first driven gear, directly to carry out, for the transmission of the rotating force between above-mentioned crankshaft and above-mentioned second driven shaft, be between above-mentioned first actuation gear and above-mentioned second driven gear, to carry out via above-mentioned second actuation gear.

In the present invention, the so-called rotating force that transmits between crankshaft and first, second driven shaft is to comprise that rotating force with crankshaft is delivered to the situation on first, second driven shaft, and will the rotating force from first, second driven shaft be delivered to the situation on the crankshaft.The previous case for example is running shaft, the balace weight axle of lubricating pump, and latter event for example is the foot pedal starting axle.

Technological scheme 2 described inventions, in technological scheme 1, it is characterized in that, above-mentioned first actuation gear is the cylindrical object that has formed outer peripheral teeth (external gear) on outer circumferential face, and be fixed on the above-mentioned crankshaft by being pressed into, above-mentioned second actuation gear is the ring-type object that has formed interior all teeth (internal gear), outer peripheral teeth (external gear) on inner peripheral surface, outer circumferential face, and this internal gear is coupled to removably on the portion of the being engaged part of above-mentioned outer peripheral teeth of above-mentioned first actuation gear.

Technological scheme 3 described inventions, in technological scheme 1, it is characterized in that, above-mentioned first actuation gear is to have outer peripheral teeth on outer circumferential face, and the cylindrical object of the external splines that is attached thereto, and be fixed on the above-mentioned crankshaft by being pressed into, above-mentioned second actuation gear is the ring-type object that has internal spline, outer peripheral teeth (external gear) on inner peripheral surface, outer circumferential face, and this internal spline is coupled to removably on the above-mentioned external splines of above-mentioned first actuation gear.

Technological scheme 4 described inventions, in any one of technological scheme 1 to 3, it is characterized in that, the internal diameter in the crank box side bearing hole of the crank journal bearing that connects near the external diameter of above-mentioned first actuation gear set for is little, under the state that unloads above-mentioned second actuation gear, above-mentioned crank box side bearing hole can be coupled on the above-mentioned crank journal bearing.

Technological scheme 5 described inventions, in any one of technological scheme 1 to 4, it is characterized in that, the crankshaft parts are installed in removably on the outside of above-mentioned first, second actuation gear of above-mentioned crankshaft, under the state that these crankshaft parts are unloaded, above-mentioned second actuation gear can unload from crankshaft.

Technological scheme 6 described inventions, in any one of technological scheme 1 to 5, it is characterized in that, be engaged with the foot pedal starting gear train that the rotation of above-mentioned foot pedal starting axle is delivered to above-mentioned crankshaft on above-mentioned first actuation gear, the rotation that is engaged with on above-mentioned second actuation gear the above-mentioned crankshaft of plate is delivered to balace weight shaft balancing device gear train.

Technological scheme 7 described inventions, in technological scheme 6, it is characterized in that, on above-mentioned first actuation gear, be engaged with rotation with above-mentioned crankshaft and be delivered to the pump gear group of lubricating pump and the rotation of foot pedal starting axle is delivered to the above-mentioned foot pedal starting gear train of above-mentioned crankshaft, the part of this foot pedal starting gear train and pump gear group is shared.

Description of drawings

Fig. 1 is the left side view that has loaded according to the motorcycle of the motor of an embodiment of the invention;

Fig. 2 is the cross sectional plan view (the II-II line sectional drawing of Fig. 6) of the deployed condition of the above-mentioned motor of expression;

Fig. 3 is the cross sectional plan view of part of stepless speed changing mechanism, the centrifugal clutch mechanism of above-mentioned motor;

Fig. 4 is the right side view of above-mentioned motor;

Fig. 5 is the left side view of above-mentioned motor;

Fig. 6 is the right side view of the state of the stepless speed changing mechanism that unloads above-mentioned motor, centrifugal clutch mechanism;

Fig. 7 is the right side view of the crank box of above-mentioned motor;

Fig. 8 is the cross-sectional rear view (sectional drawing of the VIII-VIII line of Fig. 5) of the crank box of above-mentioned motor;

Fig. 9 is the sectional drawing (the IX-IX line sectional drawing of Fig. 5) of the pedal-start device of above-mentioned motor;

Figure 10 is the sectional drawing of above-mentioned pedal-start device;

Figure 11 is the cross sectional plan view in the lubricant oil path of the above-mentioned motor of expression;

Figure 12 is the sectional drawing of above-mentioned centrifugal clutch mechanism;

Figure 13 is the side view of above-mentioned centrifugal clutch mechanism;

Figure 14 is the amplification profile of the major component of above-mentioned centrifugal clutch mechanism;

Figure 15 is the amplification profile of the major component of above-mentioned centrifugal clutch mechanism;

Figure 16 is the sectional drawing of the general driven pulley of prior art;

Figure 17 is the diagram of variation of the cooperating structure of first, second actuation gear of expression in the above-mentioned mode of execution;

Figure 18 is the diagram of other variation of the cooperating structure of first, second actuation gear of expression in the above-mentioned mode of execution.

Embodiment

Below, based on the description of drawings embodiments of the present invention.

Fig. 1 to Figure 15 is the figure that is used to illustrate according to the motor vehicular engine of an embodiment of the invention, Fig. 1 is the left side view of motorcycle that has loaded the motor of present embodiment, Fig. 2 is a cross sectional plan view (the II-II line sectional drawing of Fig. 6) of representing motor with deployed condition, Fig. 3 is the stepless speed changing mechanism of motor, the cross sectional plan view of centrifugal clutch mechanism part, Fig. 4, Fig. 5 is the right side view of motor, left side view, Fig. 6 is the stepless speed changing mechanism of unloaded engine, the right side view of the state of centrifugal clutch mechanism, Fig. 7 is the right side view of crank box, Fig. 8 is the cross sectional plan view (the VIII-VIII line sectional drawing of Fig. 5) of crank box, Fig. 9 is the cross sectional plan view (the IX-IX line sectional drawing of Fig. 5) of the pedal-start device of motor, Figure 10 is the axial cross sectional plan view of foot pedal starting, Figure 11 is the cross sectional plan view in the lubricant oil path of expression motor, Figure 12, Figure 13 is the sectional drawing of centrifugal clutch mechanism, side view, Figure 14, Figure 15 is the amplification profile of the major component of centrifugal clutch mechanism.In addition, said in the present embodiment all around refers to all around of seeing under the state of taking one's seat on the seat.

In the drawings, the motorcycle of the motor 2 of present embodiment has been loaded in 1 expression, and its general configuration is: utilize the preceding pipe 3 on the front end that is fixed on vehicle body frame 1a, but the front fork 5 that front-wheel 4 left-right rotation ground axle suspensions are supported by axle; Utilization is fixed on the back arm support 6 on the central part, trailing wheel 7 postbrachium 8 that ground axle suspension is supported by axle that can fluctuate; The vehicle seat 9 that the 9b of seat portion that 9a of seat portion that is used by the driver in the configuration of the top of above-mentioned vehicle body frame 1a and rear portion occupant use forms.

The left and right top tube 1c that above-mentioned vehicle body frame 1a is extended obliquely upward by the rear end of managing the 3 left and right down tube 1b that extend to oblique below in the past and following described each down tube 1b, and set up the left and right sides vehicle seat horizontal bar 1d that down tube 1b and top tube 1c are combined along fore-and-aft direction and constitute.In addition, above-mentioned vehicle body frame 1a is surrounded by the resin system vehicle body cover 10 that is made of front shroud 10a, legging cover 10b, side cover 10c etc.

In the upper end of above-mentioned front fork 5, be fixed with steering tiller 11, this steering tiller 11 is surrounded by handle cover 11a.In addition, between above-mentioned postbrachium 8 and back arm support 6, set up back cushion pad 12.

Above-mentioned motor 2 is air-cooling type four-cycle, single-cylinder engines, and the mode of about 45 degree is by the rear and low part of suspension support at above-mentioned down tube 1b so that cylinder axis A forwards tilts.This motor 2 includes engine main body 15, triangle belt stepless speed changing mechanism 16 and Wet-type multi-disc centrifugal clutch mechanism 17 and reduction gear 18.

Above-mentioned engine main body 15, its general configuration is, cylinder head 20 is connected to this cylinder block 19 on the mating face in, at the upside of this cylinder head 20 cylinder head cover 21 is set, on the following mating face of said cylinder body 19, connect the crank box 22 that holds crankshaft 28.

In the back of said cylinder lid 20, offer the suction port 20b that is communicated with the recess 20a that burns, on this suction port 20b, be connected with Carburetor 23 via suction tude 23a.In addition, offer the relief opening 20c that is communicated with the recess 20a that burns, on this relief opening 20c, be connected with outlet pipe 24 in the front of said cylinder lid 20.The oblique back upper place of right direction that this outlet pipe 24 is connected to the below of the speed changer case 45 that extends, describes in the back to the right tiltedly below of motor 2 and the protuberance 22b by oil chamber 95 is extended, is configured on the baffler 25 of right side side of trailing wheel 7.Spark plug 30 is inserted in the above-mentioned burning recess 20a.

On the left side of said cylinder body 19, be formed with chain chamber 19a with crank box 22 inside and cylinder head 20 internal communication, in this chain chamber 19a, dispose timing chain 34, utilize these camshaft 31 driven for opening and closing suction valves 32, outlet valve 33 by above-mentioned crankshaft 28 rotation drive cam shaft 31.

In the cylinder bore of said cylinder body 19, can insert with being free to slide and dispose piston 26.The small end 27b of connecting rod 27 is connected on this piston 26, and the big end 27a of this connecting rod is connected on the crank pin 29 that embeds between left and right sides crank arm 28a, the 28b that is installed to above-mentioned crankshaft 28.

At the rear of above-mentioned crankshaft 28, dispose variable-speed shaft 47 abreast with this crankshaft 28, dispose output shaft 48 in the left side of the axial direction of this variable-speed shaft 47 to become coaxial mode.In the left part of this output shaft 48 driving sprocket wheel 49 is installed, this driving sprocket wheel 49 is connected on the driven sprocket 51 of above-mentioned trailing wheel 7 via chain 50.

Generator 42 is installed on the left end of above-mentioned crankshaft 28.The structure of this generator 42 is when rotor 42a being fixed on the sleeve 43 of taper fit to crankshaft 28, will to be fixed on the generator casing 44 with the stator 42b of this rotor 42a subtend.

Above-mentioned crank box 22 is divided into first case 40 and second case 41 of right side in crankshaft direction left side.In this crankshaft direction of first case 40 outside, the generator casing 44 of accommodating above-mentioned generator 42 is installed removably, the crankshaft direction outside above-mentioned second case 41 is equipped with the speed changer case 45 of accommodating above-mentioned stepless speed changing mechanism 16.

The cutting lines B of above-mentioned first, second case 40,41 is offset slightly to the left than cylinder axis A.This first, second case 40,41 has and roughly is being integrally formed first, second abutment wall 40b of supporting crankshaft 28, the general configuration of 41b to the inboard of first, second periphery wall 40a, the 40b of crankshaft direction outer openings.

The first above-mentioned first case 40 abutment wall 40b, comprise the first crank abutment wall 40c of portion, and give prominence to the stair-stepping reducing gear abutment wall 40d of portion of formation in crankshaft direction left side with respect to this first crank abutment wall 40c via the left crankshaft neck 28c of left-hand axis journal bearing 35 supporting crankshafts 28.

In addition, the second above-mentioned second case 41 abutment wall 41b, comprise the second crank abutment wall 41c of portion, and give prominence to the stair-stepping clutch abutment wall 41d of portion of formation in crankshaft direction left side with respect to this second crank abutment wall 41c of portion via the right crankshaft neck 28d of right-hand axis journal bearing 36 supporting crankshafts 28.

Simultaneously, in the crank chamber 37 of utilizing above-mentioned first, second crankshaft abutment wall 40c of portion, 41c to form, contain crankweb 28a, 28b and the crank pin 29 of above-mentioned crankshaft 28.

In addition, in the clutch chamber 38 of utilizing above-mentioned second periphery wall 41a and the clutch abutment wall 41d of portion to form, contain above-mentioned centrifugal clutch mechanism 17, this clutch chamber 38 demarcates with above-mentioned crank chamber 37.

And then, in the reduction chamber 39 of utilizing above-mentioned reducing gear abutment wall 40d of portion and the clutch abutment wall 41d of portion to form, containing above-mentioned reduction gear 18, this reduction chamber 39 is communicated with above-mentioned crank chamber 37.

When this reduction gear 18 sets up deboost axle 52 abreast with variable-speed shaft 47 between the above-mentioned abutment wall 40d of portion, 41d, utilize the right side of the above-mentioned clutch abutment wall 41d of portion, utilize the recess 40e that is formed on the above-mentioned reducing gear abutment wall 40d of portion via 54 supportings of speed reduction bearing left part via this deboost axle 52 of 53 supportings of speed reduction bearing.Its structure is in addition, elementary reduction pinion teeth 74 can be installed on the variable-speed shaft 47 that is positioned at clutch chamber 38 with the relative rotation, utilize key to cooperate the elementary deceleration gearwheel 75 that will be engaged on the elementary reduction pinion teeth 74 to be attached on the above-mentioned deboost axle 52, when being integrally formed secondary reduction pinion teeth 52 on the deboost axle 52 that is positioned at above-mentioned reduction chamber 39, be integrally formed the secondary deceleration gearwheel 48a that is engaged on the secondary reduction pinion teeth 52a on the above-mentioned output shaft 48.

Above-mentioned output shaft 48 be configured in variable-speed shaft 47 same axis on.Be provided with the bearing hole 48b of the left part 76 of inserting above-mentioned variable-speed shaft 47 in the right part of this output shaft 48, via the bearing 76 that is installed in this bearing hole 48b, with the right part of this output shaft 48 of 47 supportings of variable-speed shaft recessedly.In addition, first case 40 the reducing gear abutment wall 40d of portion is run through in the left part of above-mentioned output shaft 48, and utilizes the 40d of this abutment wall portion to be supported by axle via bearing 77.Above-mentioned driving sprocket wheel 49 is fixed on the outstanding end of above-mentioned output shaft 48.

The structure of above-mentioned triangle belt stepless speed changing mechanism 16 is, drive pulley 55 is installed to above-mentioned crankshaft 28 right outer end in, driven pulley 56 is installed to the right outer end of above-mentioned variable-speed shaft 47, described two belt pulleys 55,56 is connected by coiling vee belt 57.

Above-mentioned vee belt 57 is with the resin manufacture with heat resistance, durability, in more detail, has following structure.For example, will carbon fiber or aromatic polyamide fiber be blended in the polyamide resin and a plurality of resin mass 57a of forming horizontal H shape dispose side by side, a pair of connector element 57b of the ring-type of super heat resistant rubber system is cooperated with it, they are coupled together.

Above-mentioned drive pulley 55 has the fast pulley halfbody 55a on the right part that is fixed to above-mentioned crankshaft 28, and can in axial direction slide and be configured in the movable half-pulley 55b of the crankshaft direction inboard of this fast pulley halfbody 55a via slip collar 59 with the mode of crankshaft 28 rotation.Be installed on the right part of above-mentioned crankshaft 28 by spline fitted cam disk 58, slip collar 59, said fixing half-pulley 55a be installed, and utilize locking nut 60 fastened fixing in their the axial direction outside.Between above-mentioned movable half-pulley 55b and above-mentioned cam disk 58, dispose columnar equilibrium block 61.Along with the rotation of crankshaft 28 is accelerated, equilibrium block 61 is by centrifugal force side shifting to radial direction outside, and makes movable half-pulley 55b side shifting to axial direction outside, and whereby, the diameter increase is with in scratching of belt pulley, dwindles reduction speed ratio.

Above-mentioned driven pulley 56 has the fast pulley halfbody 56a on the right outer end that is fixed to above-mentioned variable-speed shaft 47, and the movable half-pulley 56b that is configured in the crankshaft direction outside of this fast pulley halfbody 56a in the mode that can in axial direction slide.Be fixed to slip collar cylindraceous 62 spline fitted on the axis central part of said fixing half-pulley 56a to variable-speed shaft 47, the lug boss cylindraceous 63 of the axis central part that is fixed on above-mentioned movable half-pulley 56b can in axial direction be installed on this slip collar 62 movably.Setting is arranged on the pilot pin 64 on the above-mentioned slip collar 62, with slidably and this movable half-pulley 56b mode of rotating with fast pulley halfbody 56a be coupled to and forming on the sliding-groove 63a of slit-shaped on this lug boss 63.

Utilize circlip 65a will be installed to the front end of above-mentioned slip collar 62 by the spring bracket member 65 that annular slab constitutes, and between this spring bracket member 65 and above-mentioned movable half-pulley 56b, be provided with at ordinary times the helical spring 67 that will this movable half-pulley 56b loads to fast pulley halfbody 56a side.

Simultaneously, above-mentioned driven pulley 56 inserts configuration in the mode in the front end 62a of the above-mentioned slip collar 62 that submerges, and utilizes screw-thread fit to be fixed on the above-mentioned variable-speed shaft 47 to the locking nut 66 on the front end 47a of above-mentioned variable-speed shaft 47.

Here, set for the internal diameter of above-mentioned slip collar 62 stepped and, set the front end 47a of variable-speed shaft 47 for stair-stepping minor diameter greater than the major diameter of the external diameter of variable-speed shaft 47.Whereby, above-mentioned locking nut 66 and packing ring 66a can not had obstacle ground insert and be configured in the slip collar 62, like this, can make above-mentioned locking nut 66 be positioned at spring bracket member 65 than helical spring 67 in crankshaft direction inboard.

According to present embodiment, owing to will be installed in the crankshaft direction outside that the movable half-pulley 56b of the driven pulley 56 on the variable-speed shaft 47 is configured in fast pulley halfbody 56a, so, can guarantee idle space at driven pulley 56 inside parts of above-mentioned variable-speed shaft 47, and utilize this idle space, centrifugal clutch mechanism 17 can be disposed in the mode with said fixing half-pulley 56a adjacency.Whereby, needn't enlarge the width of motor, just output shaft 48 can be configured in coaxially the opposition side of the driven pulley 56 of above-mentioned variable-speed shaft 47, consequently, compare with the rear side that in the prior art output shaft is configured in variable-speed shaft, can shorten the front and back length of motor.

In the present embodiment, owing to being submerged to the axial direction inboard than the spring bracket member 65 that supports helical spring 67, disposes on above-mentioned nut 66, this helical spring 67 loads above-mentioned movable half-pulley 56b to fast pulley halfbody 56a side, so, when can guarantee the necessary length of helical spring 67, dwindle overhang with simple structure, and can suppress the maximization of motor along the size of the width direction of car to the variable-speed shaft direction outside.

That is, for example, as shown in figure 16, utilizing locking nut 203 with the exterior edge face of slip collar 201 under the fastening situation that is fixed to the structure on the variable-speed shaft 200, speed changer case 204 is to the outstanding amount that is equivalent to locking nut 203 in the outside of the width direction of car.Relative therewith, in the present embodiment,, be positioned at the inboard of axial direction because locking nut 66 is compared with the outer end of spring bracket member 65, so, the overhang of speed changer case 45 can be dwindled the amount that is equivalent to t (about 10mm).

In addition, because above-mentioned helical spring 67 is positioned at the outside of axial direction, so, under the situation of the maintenance of carrying out helical spring 67 or replacing, only need unload circlip 65a and get final product, can easily operate.Incidentally,, be about under the situation of inboard that helical spring is configured in axial direction, whole driven pulley must be unloaded and operating characteristics is low in the inboard that movable half-pulley is configured in fast pulley.

Above-mentioned speed changer case 45 is and the above-mentioned crank box 22 independent roughly airtight structures that form, from right side side's observation (with reference to Fig. 4), is the most ellipse of the upside that covers above-mentioned crank box 22.Above-mentioned speed changer case 45 is made of the lid 45b to the aluminum alloy system of the resinous box main body 45a that the under casing shape is arranged of crankshaft direction outer openings and hermetic inaccessible this opening, and utilizes that bolt 70 is fastening together to be fixed on above-mentioned second the case 41.Between the diapire 45c of above-mentioned box main body 45a and second case 41, be provided with gap a, utilize this gap a to suppress heat transfer from motor to speed changer case 45.

In the outside of the axial direction of the second periphery wall 41a that forms above-mentioned clutch chamber 38, form and have and centrifugal clutch mechanism 17 can be taken out the opening 41e of the size that put into.Clutch cover (clutch opposite side abutment wall) 71 hermetic is installed on this opening 41e, and utilizes bolt 72 with the fastening removably edge of opening portion that is fixed to the above-mentioned second periphery wall 41a of this clutch cover 71.Whereby, by speed changer case 45 and driven pulley 56 are unloaded together, and clutch cover 71 is taken off, centrifugal clutch mechanism 17 and variable-speed shaft 47 can be unloaded together.

Above-mentioned centrifugal clutch mechanism 17 left parts by the axial direction that is installed in variable-speed shaft 47, a side of central part and the clutch bearing 80,81 of opposite side are located in the mode that can not in axial direction move and to be held.This side clutch bearing 80 is by the clutch abutment wall 41d of portion supporting, and above-mentioned opposite side clutch bearing 81 is by above-mentioned clutch cover 71 supportings.

Simultaneously, support the clutch abutment wall 41d of portion of an above-mentioned side clutch bearing 80 and speed reduction bearing 53, compare with the second clutch abutment wall 41c of portion of support right shaft bearing 36, to the skew of clutch shaft direction left side, in other words, between the first clutch abutment wall 40c of portion and the above-mentioned second clutch abutment wall 41c of portion of the above-mentioned left shaft bearing 35 of supporting.More particularly, be positioned on the cylinder axis A, perhaps than cylinder axis A slightly near the position of cutting lines B.

In addition, support the clutch cover 71 of above-mentioned opposite side clutch bearing 81, be positioned at the right outside of the more close crankshaft direction of the second clutch wall 41b of portion than the above-mentioned right shaft bearing 36 of supporting.And then, support the reducing gear abutment wall 40d of portion of the left side bearing 77 of above-mentioned output shaft 48, be positioned at the axial left-external side of the more close crank of the first clutch abutment wall 40c of portion place than the left shaft bearing 35 of supporting.

According to present embodiment, because the vee belt 57 that is wound on drive pulley 55 and the driven pulley 56 is resinous, so the heat resistance of belt itself, durability can be than the belt height of rubber system, so need not to carry out the cooling of vee belt 57.Its result can make seal structure with speed changer case 45, can prevent entering of sealing or dust.

In addition,, can dwindle the external diameter of driving, driven pulley 55,56, can correspondingly dwindle the axle base of driving, driven pulley 55,56, can make motor integral body compact more by adopting the high resin system belt 57 of durability.

In the present embodiment, because speed changer case 45 is made and crank box 22 seal structure independently, so, the isolated engine thermal of the gap a that produces between two casees 22,45 utilized, heat from motor 2 is difficult to be delivered to speed changer case 45, can suppress the indoor temperature of belt and rise.In addition, because above-mentioned box main body 45a also is by the resin manufacture that is not easy to conduct heat, so, can suppress the heat transmission of starting pusher side from above-mentioned.

Above-mentioned crank box 22 is divided into first, second case 40,41 along the crankshaft direction, and above-mentioned speed changer case 45 is configured in second case 41 the axial outside of crank, also centrifugal clutch mechanism 17 is configured near the crankshaft direction inboard of this speed changer case 45, therefore, output shaft 48 can be configured in coaxially opposition side with the stepless speed changing mechanism 16 of variable-speed shaft 47, can be in the expansion of the width dimensions that suppresses motor 2, the size of dwindling fore-and-aft direction.

In addition, be installed to a side of variable-speed shaft 47, the above-mentioned centrifugal clutch of clutch bearing 80, the 81 clampings mechanism 17 of opposite side owing to utilize, so, do not need to use other parts, can utilize simple structure with centrifugal clutch mechanism 17 positioning support in axial direction.

In the present embodiment, owing to make the clutch side bearing wall 41d of supporting one side clutch bearing 80 be positioned at the left side of supporting crankshaft 28, right shaft bearing 35,36 first, the second crank abutment wall 40c, between the 41c, and the clutch cover (clutch opposite side abutment wall) 71 that makes supporting opposite side clutch bearing 81 is positioned at the crankshaft direction outside of the second crank abutment wall 41c of support right shaft bearing 36, so, with make the first crank abutment wall 40c, clutch one side bearing wall 41d reaches the second crank abutment wall 41c to each other, the situation that clutch cover 71 is positioned on the same straight line is each other compared, when can shorten the axle base of crankshaft 28 and variable-speed shaft 47, guarantee the volume of clutch chamber 38, and can accommodate centrifugal clutch mechanism 17 compactly, and then can make whole motor compact more.

In addition, because on above-mentioned second case 41 opening 41e, clutch cover 71 has been installed removably, so, by taking off speed changer case 45 and clutch cover 71, can together centrifugal clutch mechanism 17 be unloaded with variable-speed shaft 47, and can easily keep in repair or the part replacement operation.

In the present embodiment, because output shaft 48 is configured in variable-speed shaft 47 and opposition side speed changer case 45 in coaxial mode, and driving sprocket wheel 49 is installed on this output shaft 48, so, centrifugal clutch mechanism 17 and driving sprocket wheel 49 can be configured in coaxial on, the size that can dwindle the fore-and-aft direction of motor.

Above-mentioned centrifugal clutch mechanism 17 is near the inboard configuration of the crankshaft direction of driven pulleies 56.Because this centrifugal clutch mechanism 17 is the Wet-type multi-disc formula, so, mainly as Figure 12～shown in Figure 15, its structure roughly has, the mode spline fitted of bump 83b with the outer clutch 83 of cup-shaped to rotate with variable-speed shaft 47, internal clutch 84 is configured in the inboard of the axial direction of this outer clutch 83 coaxially, with the hub portion 84a of this internal clutch 84 with mode spline fitted with above-mentioned elementary reduction pinion teeth 74 rotations.In addition, above-mentioned elementary reduction pinion teeth 74 can be installed on the variable-speed shaft 47 with rotating freely.

Outside above-mentioned in the clutch 83 configuration a plurality of outside clutch plate 85, dispose 86,86, two 85,86 of two push-pads in the mode that is positioned at its two ends and be fixed on this outer clutch 83 in the mode of rotating together with this outer clutch 83.In addition, configuration internal clutch sheet 87 between clutch plate 85 and the push-pads 86 outside above-mentioned, described each internal clutch sheet 87 is fixed on the periphery of this internal clutch 84 in the mode of rotating together with above-mentioned internal clutch 84.

The inboard of clutch 83 is formed with camming surface 83a outside above-mentioned, disposes equilibrium block 88 between the push-pads 86 in this camming surface 83a and the above-mentioned outside.This equilibrium block 88 is accompanied by centrifugal force the moving to the radial direction outside by outer clutch 83, move to the left (connecting direction of clutch) of the drawing of Figure 12 by camming surface 83a, and push mobile push-pads 86, and make outer, internal clutch sheet 85,86 become contact condition each other.In addition, in Figure 12, compare with the axis of centrifugal clutch mechanism 17, upside is represented off state, and downside is represented coupled condition.

In above-mentioned centrifugal clutch mechanism 17, be provided with and prevent clutch plate labelling machine 90.This structure that prevents labelling machine 90 is, above-mentioned outside each between the clutch plate 85 and should outer clutch plate 85 and push-pads 86 between, add outer clutch plate 85, push-pads 86 leaf spring 91 to the direction loading of mutual disengaging.

In addition, on above-mentioned each internal clutch sheet 87, insert the pin 92 that the axial direction that limits this internal clutch sheet 87 moves in the circumferential direction devices spaced apart, between each internal clutch sheet 87 of each pin 92, be equipped with to the helical spring 93 that these internal clutch sheet 87 directions separated from one another are loaded.

In the centrifugal clutch mechanism 17 of present embodiment, equilibrium block 88 along with the quickening of engine revolution by centrifugal force to clutch radially foreign side move, determine the position of its axial direction by camming surface 83a.Simultaneously, when opening operation by the closure (not shown), the rotation of motor reaches specified value when above, the mobile push-pads 86 of above-mentioned equilibrium block 88 pushings, and make outer, 85,87 crimping of internal clutch sheet, whereby, the rotation of motor is passed to output shaft 48 from variable-speed shaft 47 via reduction gear 18, by the rotation of this output shaft 48, via driving sprocket wheel 49, chain 50, rotation drives trailing wheel 7.

Be accompanied by reduction by the engine speed of the closing operation of closure, equilibrium block 88 is to the radial direction medial movement, when engine speed becomes specified value when following, the crimp force that is produced by equilibrium block 88 is disengaged, above-mentioned outer, internal clutch sheet 85,87 rotate relatively, and the rotation partition of motor is between variable-speed shaft 47 and output shaft 48.

Simultaneously, when above-mentioned clutch disconnected, when above-mentioned crimp force was disengaged, by the reaction force of leaf spring 91, outer clutch plate 85, push-pads 86 were separated from each other, and simultaneously, by the reaction force of helical spring 93, internal clutch sheet 87 breaks away from each other.

Whereby, adhesion outer, that internal clutch sheet 85,87 lubricant oil to each other causes can be avoided, the skidding of clutch can be prevented.

In addition, owing to utilize moving of the axial direction respectively sell 92 restriction internal clutch sheets 87, so,, can prevent when clutch disconnects internal clutch sheet 87 inclinations etc., also can prevent the skidding of clutch from this point.

Secondly, the lubricating oil system for above-mentioned motor 2 describes.

This lubricating oil system, its structure is, utilize oil pump 96 to suck lubricant oil in the oil chamber 95 on the bottom 22a that is formed on above-mentioned crank box 22, and force feed is fed to lubricated portions such as the bearing portion of above-mentioned crankshaft 28, camshaft 31 and slide part, and also the lubricant oil that will lubricate this lubricated portion by natural whereabouts turns back to above-mentioned oil chamber 95.

Above-mentioned oil pump 96 is configured in first case 40 bottom of crank box 22 mainly as shown in figure 11, in more detail, is installed on the inner side surface 22c that is positioned at oil chamber 95 and opposition side speed changer case 45.This oil pump 96, its structure are to utilize the 97 supporting pump shaft 96a of shell with suction port 97a, exhaust port 97b, at the outer end of this pump shaft 96a installation pump gear 98.

On above-mentioned first the case 40, form the suction path 40f that is communicated with above-mentioned suction port, this sucks path 40f via the bottom surface upper shed of oil cleaner screen 99 in oil chamber 95.In addition, on above-mentioned first the case 40, be formed with the lubricant oil feed path 40g that is communicated with above-mentioned exhaust port 97b.This feed path 40g installs oil purifier 100 halfway additional, is communicated with main feed path 44a on being formed on above-mentioned generator casing 44, and the downstream of this main feed path 44a is connected on the 44c of grease chamber that is communicated with the left side of above-mentioned crankshaft 28.

On above-mentioned crankshaft 28, be formed with the oily path 28e that is communicated with the above-mentioned 44c of grease chamber at axial direction, this oil path 28e is via being formed on tributary circuit 29a on the above-mentioned crank pin 29 in connection bearing portion 101 upper sheds of this crank pin 29 with connecting rod 27.

The lubricant oil that is sucked by above-mentioned oil pump 96 passes through feed path 40g, main feed path 44a, and is sent in the oily path 28e, and 28e is supplied to connection bearing portion 101 via tributary circuit 29a from this oil path.Be supplied to the lubricant oil of this connection bearing portion 101, by the supply oil pressure, and the centrifugal force of crankshaft 28, in crank chamber 37, disperse, the part of the lubricant oil that this disperses enters in the reduction chamber 39, and lubricated secondary reduction pinion teeth 52a, gearwheel 48a, drop to then in the oil chamber 95.

Above-mentioned oil chamber 95 is formed on the bottom 22a of above-mentioned crank box 22 in the mode of the below that is positioned at above-mentioned crank chamber 37, and then, be integrally formed the protuberance 22b (with reference to Fig. 8, Figure 11) of the below that is projected into above-mentioned speed changer case 45.This protuberance 22b is from viewed in plan, forms in the mode on the projection plane that is positioned at speed changer case 45, and the vehicle-body width direction center line D of this oil chamber 95 moves to above-mentioned speed changer case 45 lateral deviations from cylinder axis A.

According to present embodiment, because on the 22a of the bottom of crank box 22, the outstanding protuberance 22b that formed of mode with the below that is projected into speed changer case 45, so, can effectively utilize the space of the free time of speed changer case 45 belows, increase the lubricants capacity of oil chamber 95, guarantee that with the bottom of deepening case the situation of lubricants capacity compares, needn't strengthen the height dimension of motor 2.

In addition, owing to make the bottom 22a of crank box 22 be projected into the below of speed changer case 45, so, can increase the surface area of oil chamber 95, can correspondingly improve cooling performance, and then, can make the weight balancing of whole motor well.

Here, in the present embodiment, owing to adopt resinous vee belt 57, simultaneously, is independently with speed changer case 45 with crank box 22, so, compare with the situation of the rubber system of employing belt, heat resistance, the durability of belt itself can be improved, and influence can be suppressed from the heat of motor.Its result can dwindle the diameter of driving, driven pulley 55,56,45 miniaturizations of speed changer case can be provided with idle space below this speed changer case, and its result can form above-mentioned protuberance 22b and increase the capacity of lubricant oil.

Below, the lubricating structure of above-mentioned centrifugal clutch mechanism 17 is described.

Above-mentioned centrifugal clutch mechanism 17 is main as Fig. 3, shown in Figure 7, and from the observation of crankshaft right angle orientation, one is positioned at from the lubricant oil of the connection bearing portion 101 of above-mentioned connecting rod 27 and crank pin 29 zone of dispersing with overlapping.Specifically, outer, the internal clutch sheet 85,87 of centrifugal clutch mechanism 17 are configured in the position that faces crank chamber 37.

Simultaneously, on the second periphery wall 41a that divides above-mentioned crank chamber 37 and clutch chamber 38, be formed with the lubricant oil that to disperse from above-mentioned connection bearing portion 101 and import to importing opening 103 in this clutch chamber 38.

In addition, on the above-mentioned clutch abutment wall 41d of portion, be integrally formed in clutch chamber 38 inboard guide portion 104 of extending.This guide portion 104 is positioned on the elongation line of connecting crank axle 28 and variable-speed shaft 47, have roughly the lubricant oil tray portion 104a that extends at longitudinal direction with above-mentioned importing opening 103 subtends ground, and then this lubricant oil tray portion 104a the lower end, around the guide portion 104b that also extends to the below of variable-speed shaft 47 circular-arcly.This guide portion 104b is inserted in the projection of the truncated cone that constitutes internal clutch 84.

Thereby block when importing the lubricant oil that opening 103 enters by guide portion 104, periphery than above-mentioned centrifugal clutch mechanism 17 leads to it on inside part more, utilize this centrifugal clutch mechanism 17 centrifugal force, outside above-mentioned lubricant oil is supplied to, between the internal clutch sheet 85,87, simultaneously, be fed to the engaging piece (with reference to the arrow of Fig. 3, Fig. 7) of elementary deceleration gearwheel 75, small gear 74.

Lubricating structure according to the centrifugal clutch mechanism of present embodiment, import to centrifugal clutch mechanism 17 owing to will be fed to the lubricant oil of the connection bearing portion 101 of crank pin 29 and the 27a of connecting rod tip portion, so, the lubricant oil that sprays in large quantities, disperses from connection bearing portion 101 can be fed to centrifugal clutch mechanism 17, need not to be provided with special lubricant oil path, and can supply the lubricant oil of q.s to centrifugal clutch mechanism 17, and prevent sintering outer, internal clutch sheet 85,87.

In the present embodiment, because centrifugal clutch mechanism 17 is configured in the clutch chamber 38 of dividing to come out from crank chamber 37, and when the crankshaft right angle orientation is observed, be positioned at the zone of dispersing from the lubricant oil of above-mentioned connection bearing portion 101, and on the second periphery wall 41a that this clutch chamber 38 and crank chamber 37 are demarcated, formed the importing opening 103 that enters that allows lubricant oil, so, can utilize very simple structure, will import to effectively in the clutch chamber 38 from the lubricant oil of crank chamber 37.

In the present embodiment, owing to be integrally formed on the clutch abutment wall 41d of portion in clutch chamber 38 inboard guide portion 104 of extending, this guide portion 104 is made of lubricant oil tray portion 104a and guide portion 104b; This lubricant oil tray portion 104a is positioned on the elongation line of connecting crank axle 28 and variable-speed shaft 47, and roughly extend with above-mentioned importing opening 103 subtends ground, this guide portion 104b follows the lower end of this lubricant oil tray portion 104a, around to the below of variable-speed shaft 47, so and be circular-arc extension, can be more outwards, supplying lubricating oil on the internal clutch sheet 85,87.

Secondly, the pedal-start device to above-mentioned motor 2 describes.

Main as Fig. 5, Fig. 9, shown in Figure 10, below the approximate vertical of above-mentioned output shaft 48, dispose foot pedal starting axle 110 in parallelly.Observe from the crankshaft right angle orientation, this foot pedal starting axle 100, it is than the bump 40h axle supporting by first case of the part of above-mentioned driving sprocket wheel 49 more close inboards, and external lateral portion is supported by the bump 44b axle that forms in pairs on the generating hood 44.

Foot pedal starting arm 111 is installed on the outer end of above-mentioned foot pedal starting axle 110.In addition, on the inner end of foot pedal starting axle 110, can axial direction slidably spline fitted foot pedal starting gear 112 is arranged, this foot pedal starting gear 112 is positioned at first the case 40.In addition, on the inner end of above-mentioned foot pedal starting axle 110, be wound with Returnning spring 113, utilize this Returnning spring 113, foot pedal starting axle 110 is loaded to stepping on rotated position.

Between above-mentioned foot pedal starting axle 110 and crankshaft 28, dispose main jack shaft 114, secondary jack shaft 115 abreast with foot pedal starting axle 110 respectively.This main jack shaft 114 sets up and is bearing on first the case 40 and second the case 41 by axle, on this main jack shaft 114, be equipped with can with the main intermediate gear 116 of above-mentioned foot pedal starting gear 112 engagements.

Above-mentioned secondary jack shaft 115 is supported by axle by the 40j of bearing portion that is formed on first case 40, and the inside and outside end of this pair jack shaft 115 is projected into first case 40 inboard, the outside respectively.In the case inboard of this pair jack shaft 115, be integrally formed the first intermediate gear 115a that is engaged on the above-mentioned main intermediate gear 116, in the case outside second intermediate gear 117 is installed.On this second intermediate gear 117, be engaged with first crank gear of describing later 121.

By above-mentioned foot pedal starting arm 111 is stepped on, 110 rotations of foot pedal starting axle, be accompanied by this rotation, foot pedal starting gear 112 moves to axial direction, be engaged on the above-mentioned main intermediate gear 116, via first, second intermediate gear 115a, 117, be delivered to first crank gear 121, crankshaft 28 rotations.

Between the sleeve 43 of the left shaft bearing 35 of above-mentioned crankshaft 28 and above-mentioned generator 42, overrunning clutch 120, above-mentioned first crank gear (first actuation gear) 121, cam sprocket wheel 122 are installed successively from the outside.

On above-mentioned overrunning clutch 120 starting gear 120a is installed, the actuation gear 125a of starter motor 125 is connected on this starting gear 120a via idle pulley 124.This starter motor 125 disposes motor axis and crankshaft 28 abreast and is fixed on the antetheca of crank box 22.

Simultaneously, above-mentioned foot pedal starting gear 112, main intermediate gear 116 and the first intermediate gear 115a are configured on the position that is communicated with the above-mentioned oil chamber 95 of first case 40 inboard.In addition, above-mentioned second intermediate gear 117, first crank gear 121 and cam sprocket wheel 122 are configured in first case 40 the outside.

According to the pedal-start device of present embodiment, because foot pedal starting gear 112, main intermediate gear 116 and the first intermediate gear 115a are positioned at the part place that is communicated with oil chamber 95, so, can lubricate these gear meshing parts fully.

In addition, owing to the inboard that makes main jack shaft 115 from first case 40 connects laterally, the rotation of foot pedal starting axle 110 is transmitted laterally from the inboard of main jack shaft 115, be delivered to crankshaft 28 from second intermediate gear 117 in this outside via first crank gear 121, so, first crank gear 121 can be configured in the outside, can dwindle the interval of crankshaft bearing 35,36, can dwindle the bending moment and the axle supporting crankshaft 28 that produce by connecting rod 27 than crankshaft neck 28c.And then, can guarantee the configuration space of cam sprocket wheel 122, second crank gear 127, easily the layout configurations around the March arbor.That is, the rotation with foot pedal starting axle 110 in first case 240 is delivered under the situation of crankshaft 28, between left crankshaft bearing 35 and left crankweb 28a gear must be arranged, and enlarges the interval of left and right bearing 35,36, is disadvantageous for above-mentioned bending moment.

In the present embodiment, owing to above-mentioned foot pedal starting axle 110 is configured in the roughly below of the Vertical direction of output shaft 48, so, carry out the operation of stepping on of foot pedal starting arm 111 easily, simultaneously, can dwindle the front and back size of motor 2.

In addition, owing to support the inboard of width direction of car of the rear wheel drive sprocket wheel 49 of above-mentioned foot pedal starting axle 110 with the first clutch abutment wall 40d of the portion axle of crank box 22, the outside with the width direction of 44 supporting cars of generator casing, on foreign side's protruding terminus of the generator casing 44 of this foot pedal starting axle 110, foot pedal starting arm 111 is installed, so, can be with foot pedal starting axle 110, and foot pedal starting arm 111 is not configured in the best position of stepping on intrusively with rear wheel drive sprocket wheel 49.

Above-mentioned foot pedal starting axle 110 as shown in Figure 4, when when the crankshaft direction is observed, is positioned at the projection plane of the axial direction of above-mentioned speed changer case 45, and in the projection plane of the axial direction of centrifugal clutch mechanism 17.More particularly, be configured in the position of below of the approximate vertical of driven pulley 56.

Owing in this wise foot pedal starting axle 110 is configured in the opposition side of speed changer case 45, so, need not to guarantee the foot pedal starting axle configuration space in this speed changer case 45, therefore, the degree ground that the drive pulley 55 and the driven pulley 56 of above-mentioned stepless speed changing mechanism 16 can be produced small gap b (with reference to Fig. 3) is near also configuration, the length that can correspondingly dwindle the fore-and-aft direction of motor.

In addition, in the axial projection of crank that above-mentioned foot pedal starting axle 110 is configured in speed changer case 45, so, foot pedal starting axle 110 can be configured in position near crankshaft 28, and the position of stepping on easily.

In the present embodiment, because above-mentioned centrifugal clutch mechanism 17 is configured near the crankshaft direction inboard of driven pulley 56, above-mentioned foot pedal starting axle 110 is configured in the projection plane of axial direction of centrifugal clutch mechanism 17 and the below of the approximate vertical of variable-speed shaft 47, so, can utilize the free space in the centrifugal clutch mechanism projection plane, foot pedal starting axle 110 is configured in the easiest position of stepping on, simultaneously, can dwindles the front and back length of motor 2.

In the back upper place of above-mentioned crankshaft 28, dispose balace weight axle 129 abreast with this crankshaft 28.This balace weight axle 129 is bearing on first, second case 40,41 via 130,131 on balace weight bearing.Give prominence to laterally from first the case 40 the left part of this balace weight axle 129, and balace weight gear 132 is attached on this protuberance.On the interior perimembranous of this balace weight gear 132, be equipped with damping member 133.

Here, left and right crankweb 28a, the 28b of crankshaft 28 is positioned at above-mentioned balace weight bearing 130,131, and the balace weight counterweight 129a of balace weight axle 129 is between above-mentioned left and right crankweb 28a, 28b, and disposes near crankshaft 28 sides in the mode that the rotating locus with crank pin 29 overlaps.Whereby, make the balace weight axle become compact on every side.

Be pressed on first crank gear of above-mentioned crankshaft 28 (first actuation gear) 121, second crank gear (second actuation gear) 127 be installed in the mode of rotating together.Above-mentioned balace weight gear (second driven gear) 132 is engaged on this second crank gear 127.In addition, second intermediate gear 117 that the rotation of above-mentioned foot pedal starting axle 110 is delivered to the foot pedal starting gear train of crankshaft is engaged on above-mentioned first crank gear 121.And then, be engaged on above-mentioned first crank gear 121 via the pump gear 98 of above-mentioned second intermediate gear 117 above-mentioned lubricating pump 96.That is, second intermediate gear 117 as the part of pump gear group and foot pedal starting gear train by shared.

In more detail, first crank gear 121 has the thickness more than 2 times of other plate-like gear, and is pressed into securely on the periphery that is fixed to above-mentioned crankshaft 28 for form the cylindric gear of outer peripheral teeth (external gear) 121a on outer circumferential face.Above-mentioned second crank gear 127 has formed the ring-type of interior all teeth (internal gear) 127a, outer peripheral teeth (external gear) 127b on inner peripheral surface, outer circumferential face.This second crank gear 127 is installed in the mode of the portion of the being engaged part (right part) that covers above-mentioned first crank gear 121, and the outer peripheral teeth 121a that all tooth 127a are coupled to above-mentioned first crank gear 121 in it goes up (with reference to Fig. 6).Whereby, the rotation of crankshaft 28 is delivered to balace weight gear 132 from first crank gear 121 via second crank gear 127.

Here, the external diameter of first crank gear 121 is configured to the little diameter of outer edge 35b that contacts than the outer ring with the bearing hole 35a that is formed on the left crank journal bearing 35 on first case 40.Whereby, the operation in the time of can realizing being assembled into crankshaft 28 in the crank box 22 with simple structure.That is, under the state that unloads second crank gear 127, the side is mobile from left to right to make above-mentioned first the case 40, and bearing hole 35a is coupled on the left crank journal bearing 35a, then, 127 cooperations of second crank gear is installed on first crank gear 121.

In addition, be installed in overrunning clutch 120, first crank gear 121, cam sprocket wheel 122 on the above-mentioned crankshaft 28, be installed to the nut 123 on the left part of above-mentioned crankshaft 28 by binding thread, with above-mentioned sleeve 43 and the clamping movably of shaft bearing 35 axial directions.

According to present embodiment, owing to being pressed into, first crank gear 121 cylindraceous is fixed on the crankshaft 28, so, can fully guarantee this first crank gear 121 to be fixed firmly to the length that is pressed into to crankshaft 28 of first crank gear 121 on the crankshaft 28.

In addition, because the rotation of crankshaft 28 is delivered to pump gear 98 from first crank gear 121 that is firmly fixed on it, and the rotation of foot pedal starting axle 110 is delivered to crankshaft 28 via first crank gear 121, so, the transmission of the rotating force between March arbor 28 and lubricating pump 96, the foot pedal starting axle 110 reliably.

In addition, second crank gear 127 disposes in the mode in the portion that is engaged (right part) that overlaps first crank gear 121, the cylindric of length can be guaranteed to be pressed into thereby first crank gear 121 can either be formed, the elongated problem of the axial length of crank can be avoided again.

In addition, owing to adopt interior all tooth 127a with second crank gear 127 to be coupled to structure on the outer peripheral teeth 121a of first crank gear 121 removably, so, can carry out installation, the dismounting of second crank gear 127 easily.

In addition, because the little diameter of internal diameter of the outer edge 35b of the crank box side bearing hole 35a of the crank journal bearing 35 that connects near the external diameter of first crank gear 121 set for, so, can carry out easily assembling in the crank box of the crankshaft 28 under the situation of crank box 22 being made left and right segmenting structure with simple structure.Promptly, when the assembling of March arbor 28, if under the state that second crank gear 127 is unloaded, first the case 40 is coupled on the crank journal bearing 35 to crankshaft direction medial movement and with above-mentioned bearing bearing hole 35a, constitute the support of crank box 22 and crankshaft 28 whereby.

In addition, unload, above-mentioned second crank gear 127 in axial direction can be unloaded in the outside by the generator 42 than first, second crank gear 121,127 outsides, the overrunning clutch 120 that will be installed in crankshaft 28.Like this, can carry out the assembling and the dismounting of second crank gear 127 easily.Because balace weight axle 129 with 127 drivings of second crank gear, at ordinary times with identical speed rotation with the rotation of motor, so, have the danger that becomes noise source, but owing to can change second crank gear 127 easily, so, when motor is assembled, can realize taking place the second few crank gear 127 of noise and the combination of balace weight gear 132 easily.

In addition, owing to will be engaged to second intermediate gear 117 on first crank gear 121, the shared situation that is delivered to crankshaft 28 in rotation with foot pedal starting axle 110, and the situation that the rotation of crankshaft 28 is delivered to pump gear 98, so, crankshaft length can be correspondingly shortened, when can make motor width compactness, the quantity of required gear and gear shaft can be reduced.

In addition, owing in being pressed into crankshaft 28, cooperate on first crank gear 121 in interior all tooth 127a of second crank gear 127, mesh second intermediate gear 117, so, the length in the crankshaft 28 of being pressed into of first crank gear 121 be can fully guarantee, can be reliably the rotation of crankshaft 28 pump gear 98, balace weight gear 132 be delivered to.

In the present embodiment, because the structure that adopts the outer peripheral teeth 121a with first crank gear 121 to cooperate with interior all tooth 127a of second crank gear 127, so, easy while of the assembling of second crank gear 127, unloading in the time of can keeping in repair easily.That is, unload and sleeve 43, overrunning clutch 120 are unloaded, can easily above-mentioned second crank gear 127 be unloaded from first crank gear 121 by nut 123 with above-mentioned crankshaft 28.

Here, in the above-described embodiment, first actuation gear has external tooth (external gear) on its whole length, but the portion that is engaged for this first actuation gear, also can make external splines, and make second actuation gear have internal spline in the side face within it, and two splines are cooperatively interacted.In this case, can form internal gear, correspondingly, it is easy that the manufacturing of second actuation gear becomes.

And then, cooperating structure about above-mentioned first actuation gear and second actuation gear, as shown in figure 17, can respectively the 121b of the portion that is engaged of first actuation gear 121 be processed into the shape of the axle of common cross section circle, and the auxiliary section 127c of second actuation gear 127 is processed into the shape in the hole of cross section circle, utilizes key 127d again both combinations.In addition, also can be as shown in figure 18, on the outer surface of the axle of first, second actuation gear, axis hole internal surface, form par 121c, 127e, will described two par 121c, 127e cooperation, also can adopt other various structures.In addition, under the situation that adopts above-mentioned cooperating structure, making above-mentioned matching part in above-mentioned generating pusher side, is favourable for dismounting second actuation gear 127.

Above-mentioned each of the motor 2 of present embodiment has following configuration structure.

Observe from the axial direction of crankshaft,, roughly disposing variable-speed shaft 47 on the same horizontal plane, output shaft 48 at above-mentioned crankshaft 28 rears.Upside at the horizontal plane C in the axle center that comprises this crankshaft 28 and output shaft 48 disposes above-mentioned balace weight axle 129 and deboost axle 52, disposes foot pedal starting axle 110, pump shaft 96a, major and minor jack shaft 114,115 at downside.

In addition, above-mentioned foot pedal starting axle 110 is configured in the approximate vertical below of output shaft 48, and above-mentioned pump shaft 96a is configured in the approximate vertical below of balace weight axle 129.And then above-mentioned major and minor jack shaft 114,115 is configured on the straight line of connecting crank axle 28 and foot pedal starting axle 110.

According to present embodiment, since at the upside configuration balace weight axle 129 of the horizontal plane C that comprises crankshaft 28 and output shaft 48, at the pump shaft 96a of downside configuration foot pedal starting axle 110 and oil pump 96, so, can can avoid the maximization of motor with these in upper and lower balancedly configuration.That is,, have free space, utilize this spatial configuration that balace weight axle 129 is arranged at the rear side of cylinder barrel at the upside of above-mentioned horizontal plane C.Simultaneously, balace weight axle 129 since counterweight 129a with big rotating locus rotation, so, when being in the state that is immersed in the lubricant oil, the power loss that is caused by the stirring of lubricant oil increases, but in the present embodiment, balace weight axle 129 can not spread lubricant oil.In addition, at the upside of above-mentioned horizontal plane C, utilize the free space between balace weight axle 129 and the output shaft 48 to dispose deboost axle 52.In this case, be positioned at the top that is difficult to supplying lubricating oil, but because the lubricant oil that disperses from the connection bearing portion 101 of the connecting rod of crankshaft 28 is supplied to reduction gear 75 etc., so, there is not the problem of lack of lubrication.

In addition, owing to the below that above-mentioned foot pedal starting axle 110 is configured in the approximate vertical direction of output shaft 48, so, when can dwindling the front and back length of motor 2, foot pedal starting axle 110 can be configured in the position of stepping on easily.

According to technological scheme 1 described invention, because first actuation gear is fixedly mounted on the crankshaft, simultaneously, above-mentioned second actuation gear is coupled to removably on the portion's of being engaged part of this first actuation gear, more particularly, because as described in the invention of technological scheme 2, first actuation gear is pressed into is fixed on the crankshaft, interior all teeth of second actuation gear are coupled to removably on the portion's of being engaged part (end) of outer peripheral teeth of first actuation gear, the rotation of crankshaft is passed through from first actuation gear to first driven gear, and be delivered to second driven gear from first actuation gear to second actuation gear, so, can fully guarantee the fixed length to crankshaft of first actuation gear, specifically, be pressed into length, and can be reliably the rotation of crankshaft be delivered to first, second driven gear.In addition, second actuation gear is configured in the mode on the portion's of the being engaged part that overlaps onto first actuation gear, thereby, even fully guaranteeing under the situation that is pressed into length of first actuation gear, also can avoid the elongated problem of the axial length of crank.

In technological scheme 3 described inventions, because external splines is partly made by the portion of being engaged of first actuation gear, on the inner peripheral surface of second actuation gear, form internal spline, and make two spline fitted, so, needn't on the inner peripheral surface of second actuation gear, form internal gear, second actuation gear easy to manufacture.

In technological scheme 4 described inventions, because the little diameter of internal diameter in the crank box side bearing hole of the crank journal bearing that connects near the external diameter of first actuation gear set for, so, can easily carry out assembling in the crank box of the crankshaft under the situation of crank box being made the left and right structure of cutting apart with simple structure.Promptly, when the assembling of March arbor, under the state that unloads second actuation gear, if the crank box of left and right partition type is in axial direction moved, and the bearing bearing hole of this crank box is coupled on the crank journal bearing, constitute the support of crank box and crankshaft whereby.

In technological scheme 5 described inventions, because when unloading the crankshaft parts that are installed in than the outside of first, second actuation gear of crankshaft, above-mentioned second actuation gear can be unloaded in the axial direction outside, so, the assembly and disassembly of second actuation gear are easy, and for example can carry out when the noise that sends from second actuation gear is big operation when it is replaced with other parts easily.

In technological scheme 6 described inventions, because the foot pedal starting gear train is engaged on above-mentioned first actuation gear, and the balace weight gear train is engaged on above-mentioned second actuation gear, so, the rotation from the foot pedal starting axle can be delivered to crankshaft reliably via first actuation gear that is securely fixed on the crankshaft.In addition, because balace weight axle by second driving gear drives, at ordinary times with identical speed rotation with the rotation of motor, might become noise source, but owing to can easily change second actuation gear, so, in the time of can being implemented in the motor assembling easily, the few actuation gear of noise and the combination of driven gear take place.

In technological scheme 7 described inventions, since with pump gear group and foot pedal starting gear train via the gear engagement of partial common to above-mentioned first actuation gear, so, when the length of crankshaft can correspondingly be shortened, can reduce the number of required gear and the number of gear shaft.

Claims (7)

1, a kind of motor, crankshaft and first, between second driven shaft, first actuation gear via above-mentioned crankshaft side, second actuation gear and above-mentioned first, first driven gear of the second driven shaft side, second driven gear transmits rotating force, it is characterized in that, above-mentioned first actuation gear is fixedly secured on the above-mentioned crankshaft, simultaneously, with above-mentioned second actuation gear in the mode on the portion of the being engaged part that overlaps onto this first actuation gear, and be coupled to removably on this first actuation gear, transmission for the rotating force between above-mentioned crankshaft and above-mentioned first driven shaft, be between above-mentioned first actuation gear and above-mentioned first driven gear, directly to carry out, for the transmission of the rotating force between above-mentioned crankshaft and above-mentioned second driven shaft, be between above-mentioned first actuation gear and above-mentioned second driven gear, to carry out via above-mentioned second actuation gear.

2, motor as claimed in claim 1, it is characterized in that, above-mentioned first actuation gear is the cylindrical object that has formed outer peripheral teeth (external gear) on outer circumferential face, and be fixed on the above-mentioned crankshaft by being pressed into, above-mentioned second actuation gear is the ring-type object that has formed interior all teeth (internal gear), outer peripheral teeth (external gear) on inner peripheral surface, outer circumferential face, this internal gear is coupled to removably on the portion of the being engaged part of above-mentioned outer peripheral teeth of above-mentioned first actuation gear.

3, motor as claimed in claim 1, it is characterized in that, above-mentioned first actuation gear is to have outer peripheral teeth on outer circumferential face, and the cylindrical object of the external splines that is attached thereto, and be fixed on the above-mentioned crankshaft by being pressed into, above-mentioned second actuation gear is the ring-type that has internal spline, outer peripheral teeth (external gear) on inner peripheral surface, outer circumferential face, this internal spline is coupled to removably on the above-mentioned external splines of above-mentioned first actuation gear.

4, as any one described motor in the claim 1 to 3, it is characterized in that, the internal diameter in the crank box side bearing hole of the crank journal bearing that the external diameter of above-mentioned first actuation gear connects near setting for is little, under the state that unloads above-mentioned second actuation gear, above-mentioned crank box side bearing hole can be coupled on the above-mentioned crank journal bearing.

5, as any one described motor in the claim 1 to 4, it is characterized in that, the crankshaft parts are installed in removably on the outside of above-mentioned first, second actuation gear of above-mentioned crankshaft, under the state that these crankshaft parts are unloaded, above-mentioned second actuation gear can unload from crankshaft.

6, as any one described motor in the claim 1 to 5, it is characterized in that, be engaged with the foot pedal starting gear train that the rotation of above-mentioned foot pedal starting axle is delivered to above-mentioned crankshaft on above-mentioned first actuation gear, the rotation that is engaged with on above-mentioned second actuation gear above-mentioned crankshaft is delivered to balace weight shaft balancing device gear train.

7, motor as claimed in claim 6, it is characterized in that, on above-mentioned first actuation gear, be engaged with rotation with above-mentioned crankshaft and be delivered to the pump gear group of lubricating pump and the rotation of foot pedal starting axle is delivered to the above-mentioned foot pedal starting gear train of above-mentioned crankshaft, the part of this foot pedal starting gear train and pump gear group is shared.

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