CN1219985C - Switching clutch - Google Patents

Abstract

A switching clutch to prevent a large shocking torque from being transmitted to a gear transmission when engaging a switching clutch in the switching clutch which is interposed between an output shaft of an internal combustion engine and an input shaft of the gear transmission whose gear ratio can be switched by transmission manipulation and is engaged/disengaged through the switching manipulation. A damper is interposed between an output member of a switching clutch and a driven member connected to the input shaft of the gear transmission.

Description

Switch clutch

Invention field

The present invention relates to be installed in the good switch clutch of vibration-damping function between the input shaft of the output shaft of internal-combustion engine and gear-shift transmission.

Prior art

In the existing switch clutch of the clutch of carrying out clutch by the clutch operation, as the real public clear 57-29070 communique of Japan and special open put down in writing in the flat 9-264337 communique, be and the bent axle of internal-combustion engine is between the clutch housing of the input gear of output gear engagement of one and switch clutch vibration damper to be installed, combine with the input shaft one of gear-shift transmission with described switch clutch housing oncoming clutch inner ring is chimeric by spline by the polylith clutch plate.

The problem that solves

Therefore, if the output block of switch clutch combines with the input shaft one of gear-shift transmission, when switch clutch engaged, the greater impact moment of generation was easy to be passed on the gear-shift transmission so.

Be used to solve the means and the effect of problem

The present invention relates to improvement to the switch clutch that overcomes these difficult points, the invention provides a kind of switch clutch, it is installed in the output shaft of internal-combustion engine and by carrying out the clutch operation of clutch between the input shaft of the gear-shift transmission of variable speed operation switch speed ratio and by handover operation, it is characterized in that the output block of this switch clutch and with driven member that the input shaft of described gear-shift transmission links to each other between vibration damper is housed.

In foregoing invention, since the output block of switch clutch and with driven member that the input shaft of gear-shift transmission links to each other between vibration damper is housed, therefore, can absorb the variation of operating the greater impact moment that produces by the clutch of switch clutch by aforementioned vibration damper, prevent that bigger impact moment is applied on the speed change gear that power transmitted side, accomplish and prevent trouble before it happens, thereby avoided the generation of noise, shock and vibration.

Brief description of drawings

Fig. 1 is the External view that relates to single cylinder OHC4 stroke IC engine one embodiment of the invention, that be provided with multidisc clutch.

Fig. 2 is the sectional arrangement drawing of major component in this internal-combustion engine.

Fig. 3 is the sectional arrangement drawing that relates to the multiplate clutch of one embodiment of the invention.

Fig. 4 is the Action Specification figure of this multiplate clutch.

Fig. 5 is for starting the front view with the housing of automatic centrifugal clutch in the foregoing description.

Fig. 6 is this drawing in side sectional elevation that starts with the housing of automatic centrifugal clutch.

Fig. 7 is this local amplification profile that starts with the mono-directional overrun clutch of automatic centrifugal clutch.

Embodiments of the invention

Below, with reference to accompanying drawing 1 to Fig. 7 one embodiment of the present of invention are described.

The body that is installed in the single cylinder OHC4 stroke IC engine 0 in the not shown motorcycle as depicted in figs. 1 and 2, by cylinder-bore 5 point to roughly the place ahead (in Fig. 1 for right-hand, in Fig. 2 be above) substantially horizontal cylinder block 1, be configured in this cylinder block 1 front end cylinder head 2, be configured in aforementioned cylinder block 1 rear end about right hand crankshaft case 3 and the left hand crankshaft case 4 cut apart constitute.Right hand crankshaft case 3 and the left hand crankshaft case 4 cut apart about described are together with each other by not shown bolt, simultaneously, by connect cylinder head 2 and cylinder block 1 from car body the place ahead and be threaded in right hand crankshaft case 3 and left hand crankshaft case 4 on bolt 6, cylinder block 1, cylinder head 2, right hand crankshaft case 3 and left hand crankshaft case 4 are combined as a whole.

In addition, as shown in Figure 2, can be inlaid in piston 7 in the cylinder-bore 5 of described cylinder block 1 with being free to slide, simultaneously, the bent axle 8 that points to vehicle-width direction is bearing on right hand crankshaft case 3 and the left hand crankshaft case 4 by ball bearing 9 free to rotately, connect described piston 7 and bent axles 8 by connecting rod 10, drive the to-and-fro motion interlock of bent axle 8 and piston 7, and in Fig. 1 rotating drive toward the clockwise direction.

In addition, in right hand crankshaft case 3 and left hand crankshaft case 4, be supported with main shaft 11 and the output shaft 12 (Fig. 1) parallel with bent axle 8 free to rotately, right-hand member at bent axle 8 is equipped with shown in Figure 3 starting with automatic centrifugal clutch 13, simultaneously, the right-hand member at main shaft 11 is equipped with the switching type clutch 36 shown in this figure.On main shaft 11 and output shaft 12, be provided with not shown gear, left end at the output shaft 12 that stretches out to left from left hand crankshaft case 4 is integrally formed with not shown driving sprocket wheel, with not shown rear wheel be that one is equipped with the driven sprocket (not shown) on the rear axle shaft of one, cross-over connection has the ring chain (not shown) on described driving sprocket wheel and driven sprocket.Under joint started state with automatic centrifugal clutch 13 and switching type clutch 36, the selectivity engagement of the gear by main shaft 11 and output shaft 12 drove not shown rear wheel with the gear ratio of regulation and rotates.

Described starting as shown in Figure 3 and Figure 4 with automatic centrifugal clutch 13, centrifugal clutch inner ring 14 is inlaid in the right side of bent axle 8 free to rotately, clutch core part 15 is positioned near the outer end of this centrifugal clutch inner ring 14, be connected the right-hand member of bent axle 8 by spline, combine with bent axle 8 one by make clutch core part 15 with the nut 16 that is threaded in bent axle 8 right-hand members.As Fig. 3 and shown in Figure 6, the retainer 18 of mono-directional overrun clutch 17 is installed between the outer circumferential face 15a of the circular depressions inner peripheral surface 14b of the outside of centrifugal clutch inner ring 14 disc portion 14a and clutch core part 15.As shown in Figure 6, in this retainer 18 along the whole roller retaining hole 18a that is formed with circumferentially, at regular intervals, in these retaining holes 18a, roller 19 is installed with loose fit, as shown in Figure 6 and Figure 7, on the outer circumferential face 15a of described clutch core part 15, be formed with clutch cam concave surface 15b.

This clutch cam concave surface 15b is as describing in detail among Fig. 7, tilt towards radial direction lenitively toward the clockwise direction from its bottom, sharply tilt to counter clockwise direction from its bottom towards radial direction, when clutch core part 15, be bent axle 8 when the clockwise direction of Fig. 6 rotates (single cylinder OHC4 stroke IC engine 0 is just changeing), the moment of rotation of clutch core part 15 can not be passed to centrifugal clutch inner ring 14, in clutch core part 15 when the counter clockwise direction of Fig. 6 is rotated (single cylinder OHC4 stroke IC engine 0 reverses), the moment of rotation of clutch core part 15 is passed to centrifugal clutch inner ring 14, or when centrifugal clutch inner ring 14 rotated in Fig. 6 toward the clockwise direction, the moment of rotation of centrifugal clutch inner ring 14 can be passed to clutch core part 15.

In addition, dispose the ring-spring 20 that is used to locate between described clutch core part 15 and retainer 18, the roller retaining hole 18a of retainer 18 can move back and forth in the position bottom the clutch cam concave surface 15b of clutch core part 15 by the spring force of this spring 20.

The bowl-shape clutch housing of being made by steel plate 21 is combined as a whole by the right side outer circumferential face of welding with clutch core part 15, and this clutch housing 21 is a formed article by press working.

It is crooked to the left that the peripheral part 21b of discoid 21a of the clutch housing 21 that forms by described drawing is approximate right angle with respect to this discoid 21a with section, simultaneously, as shown in Figure 5, circumferentially be formed with each bump 21c along whole with the interval that equates, in these bumps 21c, be formed with opening 21d near the position center of a bump 21c, simultaneously, cut out the engagement pawl 21e that is used to keep supporting ring 25 in the centre of adjacent opening 21d, discoid 21a of these clutch housings 21, peripheral part 21b, bump 21c, opening 21d, engagement pawl 21e forms when the drawing of clutch housing 21 simultaneously.

In addition, covering is positioned at the clutch core part 15 at discoid 21a center of clutch housing 21 and the lid 22 of nut 16 also is installed on discoid the 21a of clutch housing 21 by bolt 23 one, weighted cam 24 is installed in loose fit among the opening 21d of described clutch housing 21, described weighted cam 24 can freely swing the ground pivot prop up on the supporting ring 25 between discoid 21a that is held on described clutch housing 21 and the engagement pawl 21e.

On the peripheral part 14a of described centrifugal clutch inner ring 14, as shown in Figure 6, form with equal intervals along the whole circumference direction a plurality of in conjunction with recess 14c, these centrifugal clutch inner rings 14 in conjunction with recess 14c in be embedded with interior all lug boss 26a of clutch plate 26.Two side one in these clutch plate 26 are attached with friction plate 27.

In addition, as shown in Figure 3, setting-in the periphery lug boss 28a of two pressure disk 28 with clamping clutch plate 26 on the bump 21c of clutch housing 21, in these two pressure disk 28 and on the pressure disk 28 on right side, in the riveted joint of many places one guide finger 29 is arranged along the whole circumference direction to left, the tip of described guide finger 29 is inlaid in the pressure disk 28 of left side with loose fit, in described guide finger 29, be embedded with helical spring 30, in addition, the left surface in the pressure disk 28 on right side has packing ring 31 along the whole circumference direction in the riveted joint of many places one.The internal surface of the bump 21c of clutch housing 21 plays the effect of retainer, pressure disk 28 and clutch housing 21 unitary rotation.

In addition, stop or when rotating, on weighted cam 24, can not act on bigger centrifugal force, as shown in Figure 3 when bent axle 8 and clutch core part 15 are in the speed below the regulation rotational speed, clutch plate 26 and pressure disk 28 are separated from each other, thereby are in the state that clutch disconnects.

And then, when bent axle 8 and clutch core part 15 in Fig. 5 and Fig. 6 toward the clockwise direction when rotating greater than the speed of regulation rotational speed, by acting on the centrifugal force on the weighted cam 24, weighted cam 24 shown in Fig. 3 is swung toward the clockwise direction, and tilt as shown in Figure 4, the pressure disk 28 that left promotes the right side that is tilted to by described weighted cam 24, make clutch plate 26 and pressure disk 28 mutual crimping by friction plate 27, bent axle 8 is that the moment of rotation of clutch core part 15 is passed to centrifugal clutch inner ring 14 by the frictional force that is produced by described crimping.

In addition, output gear 33 is integrally formed with the left end of centrifugal clutch inner ring 14, simultaneously, adjacent this output gear 33 is provided with pair/serration wheel (セ ラ シ gear) 34, on the clutch outer 37 suitable, be formed with gear 38 with the clutch housing 21 of switch clutch 36, this gear 38 and output gear 33 and pair/serration wheel (セ ラ シ gear) 34 engagements, spring force by spring 35 usually is crimped on the non-transmission side gear of power of middle gear 38 of switch clutch 36, to eliminate the gap of the gear teeth side direction pair/serration wheel (セ ラ シ gear) 34.

And, make not shown kick starter gear or starter motor output gear and with the engagement of centrifugal clutch inner ring 14 all-in-one-piece output gears 33, if ride not shown kickpedal or start starter motor, then can on output gear 33, apply clockwise moment among Fig. 5, mono-directional overrun clutch 17 is in jointing state, drive bent axle 8 and rotate toward the clockwise direction, thereby start single cylinder OHC4 stroke IC engine 0.

In addition, flanged (FLGD) tubular body 40 connects with spline and can not be fixed on by nut 16 on the main shaft 39 of the output shaft that constitutes switch clutch 36 with extracting, the discoid moment bearing part 42 of heavy wall can be inlaid on the tube 40a of this flanged (FLGD) tubular body 40 with rotating relatively freely, and can not fix movably vertically by the spring ring 43 that engages its right side, clutch outer 37 is inlaid in the outer circumferential face of the discoid moment bearing part 42 of this heavy wall rotatably, and the spring ring 44 of the left side by engaging the discoid moment bearing part 42 of this heavy wall can not be fixed on this place vertically movably.

At the inner peripheral surface of clutch outer 37 along many of whole circumferential formation with axially extended projecting strip part 37a, on the peripheral part 45a of clutch plate 45, form the recess (not shown) that cooperates with the projecting strip part 37a of described clutch outer 37, at the central side of clutch outer 37, clutch inner ring 46 is entrenched on the tube 40a of flanged (FLGD) tubular body 40.

In addition, at the outer circumferential face of this clutch inner ring 46 along many of whole circumferential formation towards axially extended projecting strip part 46a, on the interior perimembranous 47a of pressure disk 47, be formed with the recess (not shown) that combines with the projecting strip part 46a of these clutch inner rings 46, these clutch plate 45 and pressure disk 47 are overlapping, and are clamped between the right side board 46b of moment bearing part 42 and clutch inner ring 46 to be in contact with one another.

Form the protruding 46d that protrudes to the left at the left side of clutch inner ring 46 board 46c, simultaneously, at the right lateral surface formation recess 42a of moment bearing part 42, so that moment bearing part 42 and clutch inner ring 46 can unitary rotation.

And, right side at the left side of clutch inner ring 46 board 46c, make coned disc spring 48 be installed among the tube 40a of flanged (FLGD) tubular body 40 with loose fit, be provided with spring-loaded portion 49 at the cylindrical part 46d of clutch inner ring 46 and the bight of left side board 46c, simultaneously, near the end of the tube 40a of flanged (FLGD) tubular body 40, dispose spring-loaded portion 50, to be inlaid among the tube 40a of flanged (FLGD) tubular body 40 with the spring ring 51 that described spring-loaded portion 50 combines, spring force by described coned disc spring 48, clutch inner ring 46 is to moment bearing part 42 application of forces, under normal state, clutch plate 45 and pressure disk 47 are crimped on together mutually, to engage switch clutch 36.

In addition, whole circumferential, the position formation hole 48a of interval more than 3 places in coned disc spring 48 upper edges to equate, in clutch inner ring 46, form cylindrical portion 46e in position, clutch inner ring 46 and leads component 52 are connected as a single entity by round plate 52a that runs through leads component 52 and the bolt 53 that is threaded with the cylindrical part 46e of clutch inner ring 46 corresponding to the hole 48a of coned disc spring 48.

In addition, make by bearing 54 and to draw axle and 55 be inlaid in rotationally among the cylindrical part 52b of leads component 52, functional unit 56 is connected the right-hand member that this draws axle 55, the functional unit 56 if spring force that overcomes coned disc spring 48 moves right, leads component 52 and clutch inner ring 46 are moved right with the functional unit interlock, thereby remove the mutual crimping of clutch plate 45 and pressure disk 47, switch clutch 36 is switched to off state.

In addition, on aforementioned main shaft 39 and not shown countershaft in parallel, be respectively equipped with a plurality of gears, thereby constitute gear-shift transmission.

The round plate 40b of flanged (FLGD) tubular body 40 and with the adjacent portions of moment bearing part 42 on form semicircle tubular recess 40c, 42b, between described semicircle tubular recess 40c, 42b, helical spring shock absorber 57 is housed.

Because Fig. 1 extremely embodiment shown in Figure 7 constitutes by foregoing mode, therefore, bent axle stop or with the situation of rotating less than the speed of regulation rotational speed under, as shown in Figure 3, on weighted cam 24, can not act on bigger centrifugal force, start to be in off state with automatic centrifugal clutch 13 thereby make.

If the rotating speed of bent axle 8 surpasses the regulation rotating speed, then as shown in Figure 4, by acting on the centrifugal force on the weighted cam 24, pressure disk 28 is pressed against on the clutch plate 26, start to form coupled condition, thereby make the centrifugal force of bent axle 8 be passed to the clutch outer 37 of switch clutch 36 with automatic centrifugal clutch 13.

In addition, because starting the clutch housing 21 with automatic centrifugal clutch 13 is that steel plate is carried out drawing, discoid 21a, peripheral part 21b, bump 21c, opening 21d and the engagement pawl 21e's of integrally formed clutch housing 21 of while, therefore consequently: the mould that need not a plurality of complexity, can reduce number of components and machining period, and can improve the productivity that constitutes clutch housing 21 with thin copperplate, thereby can weight reduction also reduce cost significantly.

Owing to do not acting on to right-hand steering force under the normal state of functional unit 56, switch clutch 36 is in jointing state, therefore, if the rotating speed of bent axle 8 surpasses the regulation rotating speed, owing to start also to be in jointing state, also can drive main spindle 39 rotate with automatic centrifugal clutch 13.

Like this, under the situation (Fig. 4) of starting with automatic centrifugal clutch 13 and switch clutch 36 formation jointing states, if to right-hand operating operation parts 56, then switch clutch 36 is in off state, running torque can not be passed on the main shaft 39, is separately positioned on main shaft 39 and is adjacent gear meshing on the countershaft that be arranged in parallel thereby optionally switch.Afterwards, the opening operation by carrying out switch clutch 36 and the variable speed operation of gear-shift transmission, not shown motorcycle can travel with desired gear ratio.

In addition, because gear 38 is integrally formed on the clutch outer 37 of switch clutch 36, therefore, can shorten all axial dimensions of switch clutch 36, reduce the number of components of switch clutch 36, simplified structure, realize miniaturization and weight reduction, and also can reduce cost.

And, from starting to be applied to the variation of the moment on the clutch outer 37 of switch clutch 36 with automatic centrifugal clutch 13, after mutual slip by clutch plate 45 and pressure disk 47 is absorbed, further absorbed by the helical spring shock absorber of between flanged (FLGD) tubular body 40 and moment bearing part 42, installing 57, therefore, on the tooth that is arranged at the gear on main shaft 39 and the not shown countershaft, can not act on bigger moment variations, thereby improve the serviceability of tooth on the gear.

Because what produce when switch clutch 36 engages is absorbed by helical spring shock absorber 57 than the large driving force square, therefore, the impact force that is produced by the handover operation of switch clutch 36 is difficult to be passed to input power from this switch clutch 36 and is transmitted on the gear-shift transmission of side.

In the above-described embodiments, though the situation that structure of the present invention is used for the multidisc switch clutch is illustrated, structure of the present invention is not limited to the multidisc switch clutch, also is suitable for for the switch clutch of other form.In addition, in the above-described embodiments, though provided the situation of spring as vibration damper, vibration damper is not limited to spring, also can adopt the vibration damper that has utilized hydraulic pressure.

Claims (1)

1. switch clutch, be installed in the output shaft of internal-combustion engine and, it is characterized in that by carrying out the clutch of clutch between the input shaft of the gear-shift transmission of variable speed operation switch speed ratio and by handover operation: the output block of this switch clutch and with driven member that the input shaft of described gear-shift transmission links to each other between vibration damper is housed.

Images