CN1055751C - Clutch structure - Google Patents
Clutch structure Download PDFInfo
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- CN1055751C CN1055751C CN95117662A CN95117662A CN1055751C CN 1055751 C CN1055751 C CN 1055751C CN 95117662 A CN95117662 A CN 95117662A CN 95117662 A CN95117662 A CN 95117662A CN 1055751 C CN1055751 C CN 1055751C
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Abstract
The present invention provides a clutch wherein the connection and disconnection of the power transmission between a clutch input shaft 5 and a clutch output shaft 2 is carried out by spreading and contracting the interval between a clutch center 8 and a pressure plate 9 on the clutch output shaft 2 side. The clutch structure is equipped with the reverse torque limitter mechanisms 20 and 25 for shifting the pressure plate 9 in the direction for spreading an interval for the clutch center 8 by the input of the reverse torque and a limitter cancellation mechanism 40 and 42 for carrying out control so that the reverse torque limitter mechanism does not operate when the number of revolution of the clutch center 8 is less than that in idling.
Description
The present invention relates to a kind of vehicle friction clutch, especially go up, the present invention relates to a kind ofly have by vehicle friction clutch from the clutch control mechanism of the opposing torque of clutch output shaft one side.
Have the opposing torque limting mechanism in clutch, to prevent that when the situations such as downshift, engine transmits excessive opposing torque from trailing wheel, this type of example has all motions (special open 5-73928 communique, spy open clear 59-219525 communique etc.) in the past.
In these examples, when the input opposing torque, the pressure plate of friction clutch has so just weakened the frictional engagement of clutch towards moving away from the clutch core direction.
Though in real public clear 61-35807 communique, such example is being arranged: having pin and stepping in foot-on mechanism two-wheeled, pin step on foot-on moment by clutch transmits to bent axle, so that engine starting, but in this embodiment, if design above-mentioned opposing torque limting mechanism, then step on foot-on moment and the opposing torque limting mechanism is worked cause having weakened to the engine carry-over moment owing to pin, the engine starting can not be carried out smoothly like this, therefore, the moment limits value that the opposing torque limting mechanism is had an effect just must be set very highly, has so just limited the original function of opposing torque limting mechanism.
Below, as shown in figure 10, be one and have the example that pin is stepped on foot-on mechanism.
The following describes the general situation of this example structure.Clutch input gear 05 engagement on the clutch outer member 04 of gear that embedding on the bent axle 01 02 and friction clutch 03, be entrenched in clutch core 07 all-in-one-piece clutch output shaft 08 on gear train 09 and gear train 010 engagement that is entrenched on the jack shaft 011, like this, the driving of engine just is delivered to jack shaft 011 by friction clutch 03 from bent axle 01 together, and the rotation of jack shaft 011 is delivered to trailing wheel by chain etc.
Pin is stepped on foot-on mechanism and is constituted in the following manner.On pedal axle 015, pedal is housed, by the claw-type clutch 016 that is loaded on pedal axle 015, the idler gear 017 that can be loaded on pivotally freely on the above-mentioned jack shaft 011 can be turned round, this idler gear 017 and clutch input gear 05 all-in-one-piece gear 018 engagement with friction clutch 03.
Thereby, step on operation in case carried out pin, pin is stepped on foot-on moment and just is passed to bent axle 01 by claw-type clutch 016, idler gear 017, gear 018, gear 05 and gear 02, directly transmits without friction clutch 03.
Like this, owing to foot-on moment comes to be delivered on the bent axle 01 through friction clutch 03, even above-mentioned opposing torque limting mechanism is set on above-mentioned friction clutch 03, for the ground foot-on that is well on, also there is no need to limit the function of opposing torque limting mechanism, like this, foot-on mechanism and opposing torque limting mechanism function separately can both be brought into play fully.
But, the transfer mechanism by means of idler gear 017 must be arranged, and trailing wheel revolution is promoted, mechanism's cart, what make the engine starting is that starting can not be carried out smoothly before so-called the pushing away.
That is to say owing to push away preceding starting, during jack shaft 011 revolution, the opposing torque that produces during by the downshift situation identical transmission of torque path and having to through with input the time through friction clutch 03, therefore the opposing torque limting mechanism works, on friction clutch, skid, so just can not sufficient transmission of torque to bent axle 01, cause the starting of engine not smooth thus.
Thereby make push away before starting and opposing torque limiter and depositing, which all can not give full play to its function.
The present invention provides a kind of simply constructed clutch configuration in view of this point, and its purpose is not limit the function of opposing torque limting mechanism, and foot-on is with to compare starting originally more smooth, and starting also can more successfully be carried out before pushing away.
In order to achieve the above object, the invention provides a kind of vehicle friction clutch, it comprises clutch core, pressure plate and clutch outer member; Clutch core and pressure plate are supported on the clutch output shaft; Clamping has clutch plate and clutch friction plate between clutch core and pressure plate, and the distance between clutch core and the pressure plate can be dwindled under the effect of disc spring, to carry out the transmission of power of clutch; Described clutch is provided with cam mechanism, under the input action of the opposing torque of clutch output shaft side, cam mechanism makes the relative displacement that produces gyratory directions between clutch core and the pressure plate, and the distance between above-mentioned clutch core and the above-mentioned pressure plate is enlarged; It is characterized in that: described clutch has ratchet and pawl arrangement, and when the winding number when the winding number of above-mentioned clutch core is idle running was following, above-mentioned cam mechanism was failure to actuate, thereby has limited the relative displacement between above-mentioned clutch core and the above-mentioned pressure plate.
Particularly, described cam mechanism has: the cam recess, and its rear side at gyratory directions is darker, then slowly shoals glossily in the front side of gyratory directions; Sell with promoting, it is arranged on the clutch core, and facing to the cam recess, described ratchet and pawl arrangement has: the ratchet plate, and it is provided with the stop lug boss; With the recoil equilibrium block, it is provided with the stop arm, can joltily with pivotal mounting, and the front end of stop arm can withstand on the stop lug boss.
Particularly, the cardinal extremity of described disc spring is fixed, and free end withstands on a side of pressure plate.
In addition, the invention provides a kind of vehicle friction clutch, comprise clutch core, pressure plate and clutch outer member; Clutch core and pressure plate are supported on the clutch output shaft; Clamping has clutch plate and clutch friction plate between clutch core and pressure plate, and the distance between clutch core and the pressure plate can be dwindled under the effect of disc spring, to carry out the transmission of power of clutch; Described clutch is provided with cam mechanism, under the input action of the opposing torque of clutch output shaft side, cam mechanism makes the relative displacement that produces gyratory directions between clutch core and the pressure plate, and the distance between above-mentioned clutch core and the above-mentioned pressure plate is enlarged; It is characterized in that: described clutch has bindiny mechanism, when the winding number when the winding number of above-mentioned clutch core is idle running is following, above-mentioned bindiny mechanism can make the opposing torque of clutch output shaft side be delivered to the Clutch input shaft side, and this power transmission relationship also can disconnect.
Particularly, described bindiny mechanism has: the ratchet circle, and inner circumferential surface is provided with hook tooth; With the recoil equilibrium block, it is provided with the stop arm, can joltily with pivotal mounting, and the stop arm can withstand the tooth of above-mentioned ratchet circle.
Technique scheme of the present invention has many advantages, makes a concrete analysis of as follows now:
When winding number is following when the winding number of clutch core is idle running, because the limiter zeroing mechanism is failure to actuate the opposing torque limting mechanism, so when no matter before foot-on still pushes away, starting, the opposing torque limting mechanism all is failure to actuate, engine starting just can carry out smoothly, under steam when situation opposing torques such as running into downshift is imported, winding number when the winding number of clutch core surpasses idle running, the original function of opposing torque limting mechanism also is unlikely infringement, can prevent the revolution of crossing of engine, can prevent that the braking of engine from attacking the amount of letting slip simultaneously again.
Above-mentioned opposing torque limting mechanism is a kind of like this mechanism: above-mentioned pressure plate can relative displacement on respect to the gyratory directions of above-mentioned clutch core, make above-mentioned pressure plate be transformed into the axial relative displacement of revolution because of the opposing torque input, make the interval between above-mentioned clutch core and the above-mentioned pressure plate become big thus with respect to the relative displacement of the gyratory directions of above-mentioned clutch core.Above-mentioned limiter zeroing mechanism has the confining part that is moved by centrifugal weights in above-mentioned clutch core, when the winding number of the above-mentioned clutch core winding number during than idle running hour, above-mentioned confining part just retrains above-mentioned pressure plate with respect to the relative displacement of above-mentioned clutch core at gyratory directions, therefore in the opposing torque limting mechanism, can convert the relative displacement for the gyratory directions of clutch core to the axial relative displacement of revolution, unnecessary have an intermediate member that pressure plate is moved.Because the limiter zeroing mechanism is in the winding number at clutch center during for idle running under the situation below the winding number, confining part retrains above-mentioned pressure plate with respect to the relative displacement on the above-mentioned clutch core gyratory directions, so when no matter before foot-on still pushes away, starting, the opposing torque limting mechanism all is failure to actuate, and the engine starting just can be carried out smoothly.
Above-mentioned opposing torque limting mechanism has transform component, this transform component will be transformed into the axial relative displacement of revolution in the relative displacement of rotating direction for above-mentioned clutch core, because the input of opposing torque, above-mentioned conversion member acts on above-mentioned pressure plate, interval between itself and above-mentioned clutch core is enlarged, and above-mentioned limiter zeroing mechanism has at the confining part of above-mentioned clutch core by centrifugal weights action, the winding number of above-mentioned clutch core for the idle running winding number when following above-mentioned confining part retrain above-mentioned conversion member with respect to the gyratory directions of above-mentioned clutch core or turn round axial relative displacement.Be idle running winding number when following when the winding number of clutch core like this, the conversion member just can not take place act on pressure plate and be delivered to the situation that engine goes after starting torque is reduced that engine starts and can carry out smoothly.
Realize that by the clutch core and the distance between the pressure plate that enlarge or dwindle clutch output shaft one side the friction clutch that is transmitted into disconnection of power has opposing torque limting mechanism and bindiny mechanism between Clutch input shaft and the clutch output shaft.The opposing torque limting mechanism can lean on the input of opposing torque to make above-mentioned pressure plate and the direction that enlarges with respect to the interval of above-mentioned clutch core moves.Bindiny mechanism then can make when following above-mentioned Clutch input shaft be connected with drive transmitting between the above-mentioned clutch output shaft for the idle running winding number or disconnects in the winding number of above-mentioned clutch output shaft.
When the winding number the when winding number of clutch core is idle running is following, since bindiny mechanism Clutch input shaft with on clutch output shaft is connected, so be foot-on or push away before when starting one opposing torque limting mechanism all be failure to actuate, engine can start smoothly.Travel opposing torque when input under situations such as downshift, winding number when the winding number of clutch output shaft has surpassed idle running, the connection of above-mentioned bindiny mechanism is disengaged, the original function of opposing torque limting mechanism is not suffered a loss, and rotatingly can prevent also that simultaneously the effect of engine break is excessive preventing that engine from crossing.
Above-mentioned bindiny mechanism is a kind of unidirectional bindiny mechanism, and it can only give Clutch input shaft with the transmission of torque of clutch output shaft, and can not carry out rightabout transmission of torque.Drawing sincere starting back connection can make the opposing torque limting mechanism work reliably with regard to easily removing, above-mentioned Clutch input shaft and above-mentioned clutch output shaft are disconnected and connect by the work of the centrifugal weights of being located at above-mentioned Clutch input shaft one side, when the winding number of above-mentioned Clutch input shaft when the idle running winding number is following, above-mentioned Clutch input shaft is connected with above-mentioned clutch output shaft, so, foot-on or push away before when starting, Clutch input shaft is with on clutch output shaft is connected, and the engine starting just can be carried out smoothly.And in travelling when situations such as downshift, the connection of bindiny mechanism is disengaged, the opposing torque limting mechanism carries out work, can prevent the revolution of crossing of engine.
Below referring to figs. 1 through Fig. 7 one embodiment of the invention are described.
Fig. 1 is the sectional drawing of the friction clutch of one embodiment of the invention.
Fig. 2 is the sectional drawing after omit on other section top of friction clutch shown in Figure 1.
Fig. 3 is the front elevation of the pressure plate in embodiment illustrated in fig. 1.
Fig. 4 is the IV-IV sectional drawing among Fig. 3.
Fig. 5 is the front view of the major component of limiter zeroing mechanism.
Fig. 6 is the pressure plate front view of other state.
Fig. 7 is the VII-VII sectional drawing among Fig. 6.
Fig. 8 is the sectional drawing of other embodiment's friction clutch.
Fig. 9 is main position, the local abridged of the limiter zeroing mechanism part front view in embodiment illustrated in fig. 8.
Figure 10 is a drive transmission mechanism sectional drawing in the past.
Among the figure,
1: friction clutch, 2: clutch output shaft, 3: bearing, 4: clutch outer member, 5: clutch input gear, 6: lining, 7: nut, 8: clutch core, 9: pressure plate, 10: clutch plate, 11: clutch friction plate, 12: disc spring, 20: cam recess, 21: tapped hole, 22: long ditch, 25: promote pin, 26: slotted hole, 27: long ditch, 30: releaser fixture supports propeller boss, 3: bolt, 32: releaser anchor clamps, 33: bearing,
35: Returnning spring, 40: ratchet plate, 41: bearing, 42: recoil equilibrium block, 43: pad, 44: flat-top screw, 45: retaining spring, 50: friction clutch, 51: lobe plate, 52: clutch outer member, 53: bearing, 54: recoil equilibrium block, 55: bolt, 56: nut, 57: retaining spring.
Fig. 1 is the sectional view of present embodiment friction clutch 1, and Fig. 2 is the sectional drawing of other section.
On the clutch output shaft 2 that in the cylinder of clutch outer member 4, stretches out with spline chimeric lining 6, tighten by nut 7 simultaneously and forbid that lining 6 is moving axially but can turn round with clutch output shaft 2 with being integral, the central cylindrical part 8a of clutch core 8 is inlaid on this lining 6.
In the cylindric inside of clutch outer member 4, in the inboard of clutch core 8, pressure plate 9 is connected by the central cylindrical part 8a of clutch core 8, axially slidably certainly also relatively pivotally free end bearing.
In the space between the cylinder inner surface of the outer surface of the cylindrical part 9b of this pressure plate 9 and clutch outer member 4, multi-disc is disposing the clutch friction plate 11 of clutch outer member 4 one sides and the clutch plate of pressure plate 9 one sides alternately.
That is to say, on the cylinder inner peripheral surface of clutch outer member 4, along the circumferential direction have the opening 4a of many points in axial direction, the periphery jut of clutch friction plate 11 is housed on opening 4a, allow vertically supporting several pieces slidably; Also there is the ditch bar 9c of points in axial direction to form several on the outer surface of the cylindrical part 9b of pressure plate 9 at circumferencial direction, the internal surface jut of clutch plate 10 is housed in the ditch bar 9c, and vertically slidably, their one piece of one piece of ground is inserted between the above-mentioned clutch friction plate 11.
These clutch friction plates 11 and clutch plate 10 all are sandwiched in again between the 9a of plectane portion of the flange 8d of clutch core 8 and pressure plate 9.
So when pressure plate 9 made the interval dwindle near clutch core 8, clutch friction plate 11 was approaching mutually with clutch plate 10, strengthened friction and connected; On the contrary, if pressure plate 9 leaves clutch core 8, when it enlarged at interval, clutch friction plate and clutch plate 10 just were separated from each other, and weakened friction and connected.
Moreover the disc spring 12 that pressure plate 9 is used as clutch spring is pushed the direction (right-hand among Fig. 1) near clutch core to, and the cardinal extremity of this disc spring must be connected on the lining 6.
The discoideus lobe plate 20 of hollow is crimped on the ring-type plectane 9a of portion of pressure plate 9 by disc spring 12, its crimping face is at the opposition side of cylindrical part 9b, the 9a of the plectane portion equal intervals ground of pressure plate 9 is provided with circular hole in 3 places, 3 nose of cam 20a that embed above-mentioned 3 circular holes are respectively arranged on this lobe plate 20, and the front-end face of nose of cam 20a that runs through the 9a of plectane portion of pressure plate 9 is provided with cam recess 20b.
Above-mentioned disc spring 12 apical graftings are crimped on the pressure plate 9 lobe plate and become one on an end of this lobe plate 20, simultaneously, pressure plate 9 toward directions pushing near clutch core 8.
As shown in Figure 3, uniformly-spaced the cam recess 20b in 3 places is forming facing on the face of clutch core 8; As shown in Figure 4, the cam recess is shaped in the following manner at the front-end face of nose of cam 20a: darker at the gyratory directions rear side, the front side then slowly shoals glossily.
In addition, as shown in Figure 3, the ring-type plectane 9a of portion of pressure plate 9 is provided with 3 equally spaced tapped holes 21, swells slightly around this tapped hole 21, forms the 21a of installation step portion of aftermentioned releaser fixture supports propeller boss 30.
Moreover on the ring-type plectane 9a of portion of pressure plate 9, the face facing to clutch core 8 as shown in Figures 2 and 3, also is provided with long ditch 22 in 3 places equally spacedly, and half of Returnning spring 35 is contained in this ditch.
Face toward on the 8b of plectane portion of pressure plate 9 in clutch core 8, corresponding to above-mentioned cam recess 20b, be equipped with and promote pin 25, and make cam recess 20b facing to 25 head, be provided with slotted hole 26 corresponding to above-mentioned tapped hole 21 at circumferencial direction, forming section facing to above-mentioned long ditch 22 is the long ditch 27 of semicircle shape.
The bolt 31 of being close to the above-mentioned installation step 21a of portion of pressure plate 9 is tightened on the tapped hole 21, and the cylindric releaser fixture supports propeller boss 30 that is designed to protrude runs through the slotted hole 26 of clutch core 8.
Be provided with releaser anchor clamps 32 near clutch output shaft 2 front ends, the bearing 33 as the releaser action part in side embedding within it, the flange 32a of these releaser anchor clamps 32 and the ratchet plate 40 of ring-type join, its 3 overlapping places join with the front end of above-mentioned 3 releaser fixture supports propeller boss 30 respectively, tighten releaser fixture supports propeller boss 30, releaser anchor clamps 32 and ratchet plate 40 fixing by above-mentioned bolt 31.
The releaser fixture supports propeller boss 30 that runs through the slotted hole 26 of clutch core 8 can move along slotted hole 26, thereby, pressure plate 9 is limited in a certain scope with respect to the relative revolution of clutch core 8, this scope is releaser fixture supports propeller boss 30 scope movably in slotted hole 26, constitutes stop mechanism thus.
At the long ditch 27 of the long ditch 22 of pressure plate 9 one sides and clutch 8 one sides the Returnning spring 35 that has compressed at circumferencial direction is housed between the two in addition, when clutch core 8 with respect to pressure plate 9 when gyratory directions advances, it is pushed toward returning original position.
As shown in Figure 5, above-mentioned ratchet plate 40 separates, forms at the part 40c that bears of gyratory directions (direction of arrow) posterior protrusion by stopper protrusion part 40b on the edge between mounting portion 40a, the 40a and with ditch.
On the flange 8d of clutch core 8, roughly corresponding to the 40b of stopper protrusion portion of ratchet plate 40 and bear on the position of the 40c of portion flat cylinder support 8e is arranged.Prop up on cylinder support 8e by bearing 41 pivots the end of recoil equilibrium block 42, by pad 43 usefulness screws 44, can joltily be installed with freely.(referring to Fig. 1).
As shown in Figure 5, recoil equilibrium block 42 stretches out equilibrium block arm 42a and catch arm 42b from its base portion to gyratory directions, and equilibrium block arm 42a is in deep position than catch arm 42b, and size is also longer.
Between this recoil equilibrium block 42 and the clutch core 8 retaining spring 45 is housed, it makes equilibrium block arm 42a and catch arm trend central shaft one side is ratchet plate 40 1 sides.
Because catch arm 42b and ratchet plate 40 axially are being in same position, so when when occasion such as stopping, the elastic force of retaining spring 45 joins catch arm 42b and ratchet plate 40.
In addition, on the outward edge precalculated position of the flange 8d of clutch core 8, be provided with chock 46 (with reference to Fig. 5),, so just limited the hunting range of recoil equilibrium block 42 so the front end of the equilibrium block arm 42a of backlash equilibrium block 42 can be run into chock 4b.
Above-mentioned recoil equilibrium block 42 combines with ratchet plate 40 grades and has just constituted the limiter zeroing mechanism.When clutch output shaft 2 and clutch core 8 shut down together or when winding number that idle running is decided is following, recoil equilibrium block 42 spring 45 that is positioned is pressed to 40 1 thrusters of ratchet plate, compare with clutch core 8, ratchet plate 40 is in the state of more going ahead of the rest on gyratory directions, catch arm 42b is connected to and bears on the 40c of portion shown in Fig. 5 solid line, the front end apical grafting of catch arm 42b like this, has just retrained the relative revolution of ratchet plate 40 with respect to clutch core 8 on stopper protrusion 40b.
Because ratchet plate 40 becomes one with pressure plate 9 by releaser anchor clamps 32, releaser fixture supports propeller boss 30, so under above-mentioned state, pressure plate 9 is under an embargo with respect to the relative revolution of clutch core 8, pressure plate 9 is in the position near clutch core 8, keeping the jointing state of clutch thus, thereby, import gear 5 by being delivered to clutch non-skidly in friction clutch 1 way that is in connection state by the moment that clutch output shaft 2 is oppositely imported.
Thereby, Kick-start with compared originally, before pushing away when starting rotating clutch output shaft 2 flywheel moment slightly loss some be delivered to clutch and import gear 5, import gear 5 from clutch and be delivered to again on the bent axle of engine, the starting of engine just can be carried out smoothly.
Then, the rotation number of clutch core 8 dallies when above surely in institute, above-mentioned retaining spring 45 does not hinder the swing laterally of recoil equilibrium block 42 owing to centrifugal force, shown in the double dot dash line among Fig. 5, recoil equilibrium block 42 shakes, make catch arm 42b be disengaged, thereby clutch core 8 can be carried out freely with the relative revolution between the pressure plate 9 with the combining of the 40b of stopper protrusion portion of ratchet plate 40.
Fig. 3 and Fig. 6 are the front elevation of the pressure plate 9 seen from clutch core 8 one sides, represent lifting pin 25, the slotted hole 26 of clutch core 8 one sides, the relative position of long ditch 27 with double dot dash line among the figure, Fig. 3 when travelling usually or the state in when acceleration, the state when Fig. 6 then represents to slow down.
When travelling usually, the clutch core 8 that is driven side will lag behind a bit than driving side, the elastic force of bounce-back spring 35 is had an effect, as shown in Figure 3, the 21a of installation step portion (releaser fixture supports propeller boss 30) is in first line position on the front end of the gyratory directions of the slotted hole 26 of clutch core 8 one sides, clutch core is turned round integratedly, promote the most recessed dark position of gyratory directions rear side (with reference to Fig. 4) that pin 25 also is in cam recess 20 with lagging behind.
Thereby, pressure plate 9 is in immediate position with respect to clutch core 8, interval between the 9a of plectane portion of the lip part 8d of clutch core 8 and pressure plate 9 has dwindled, strengthened the frictional engagement between clutch friction plate 11 and the clutch plate 9, clutch is in jointing state, and the driving of clutch input gear 5 only some kinetic equation losses are arranged slightly is delivered on the clutch output shaft 2.
During Reduced Speed Now and in the time of vehicle immobilization, clutch is bearing the opposing torque from the engine break, the clutch core 8 that becomes one with clutch output shaft 2 as driven shaft than the pressure plate 9 of engine one side on gyratory directions in advance, as shown in Figure 6, the elastic force of opposing Returnning spring 35, the slotted hole 2b of clutch core 8 one sides advances with respect to the 21a of installation step portion (releaser fixture supports propeller boss 30) of pressure plate 9 one sides, promoting pin 25 relatively moves to the gyratory directions front side of cam recess 20, as shown in Figure 7, because the effect of the recess that shoals gradually, pressure plate P toward the between centers pushing, has been produced the load of opposing disc spring 12.
Thereby, the interval that has enlarged between the 9a of plectane portion of the lip part 8d of clutch core 8 and pressure plate 9 enlarges, weakened the frictional engagement between clutch friction plate 11 and the clutch plate 10, thereby clutch can suitably skid, can alleviate excessive opposing torque and act in the clutch input gear 5 and be added on the engine, so just can prevent revolution.
In addition, the effect of engine break is excessive on the contrary also can prevent.
As mentioned above, when idle running is decided to turn round more than the winding number, engaging between recoil equilibrium block 42 and the ratchet plate 40 is disengaged, clutch core 8 is freely with relative revolution between the pressure plate 9, the opposing torque limting mechanism is had an effect, and can prevent that the effect of crossing revolution and engine formulator of engine is excessive.
Also have, at the controlled clutch controlling rod and during cut-off clutch, the interlock clutch control lever is pressed into clutch output shaft 2 one sides with releaser fixture supports propeller boss 30, by releaser fixture supports propeller boss 30, make pressure plate 9 press disc spring 12 to move towards direction away from clutch 8, frictional engagement between clutch friction plate 11 and the clutch plate 10 is disengaged, so just can cut-off clutch.
At this moment, even ratchet plate 40 is in jointing state with recoil equilibrium block 42, axially relatively move still freely.
In the structure of present embodiment, can draw with the starting of the opposing torque of clutch output shaft 2 sincere, so there is no need to have the idler gear of using for foot-on, particularly carry-over moment.
Below, according to Fig. 8 and Fig. 9 another embodiment is described.
The friction clutch 50 of present embodiment, its clutch agent structure and opposing torque limting mechanism are same as the previously described embodiments, and identical parts are represented with identical mark.
And the lobe plate 51 suitable with above-mentioned lobe plate 20 formed ratchet circle 51a, and formed hook tooth on the inner peripheral surface of this ratchet circle 51a, as shown in Figure 9 on its plectane outer rim.
Formed flat cylinder supporting 52a in the plectane portion facing to the clutch outer member 52 of the plectane portion of lobe plate 51, recoil equilibrium block 54 props up on the 52a of cylinder branch by bearing 53 pivots, and by bolt 56, nut 55 shakes freely and is installed with.
The recoil equilibrium block 54 equilibrium block arm 54a that (direction of arrow) extends long size from pivot along gyratory directions then extends the catch arm 54b of short size in the opposite direction, and catch arm 54b can engage with above-mentioned ratchet circle 51a.
On the precalculated position of the plectane of clutch outer member 52, be provided with the block 52b (referring to Fig. 9) of projection, it has limited the swing of recoil equilibrium block 51a.
Between this recoil equilibrium block 54 and clutch outer member retaining spring 57 is housed, this retaining spring 57 is equilibrium block 54 counterclockwise direction pushing in Fig. 9.Do not having other any external force to do the time spent, the indented joint of catch arm 54b and ratchet circle 51a.
But combining between catch arm 54b and ratchet circle 51a is that folk prescription is to combination, with respect to the revolution of the opposing torque of clutch output shaft 2 is the revolution of the direction of arrow of ratchet circle 51a, and promptly the recoil equidirectional relative rotation of equilibrium block 54 of clutch outer member 52 is freely; But because the combining of catch arm 54b and ratchet circle 51a, the relative reversed turning between them is under an embargo.
Thereby, when clutch outer member 52 stops or idle running decide below the winding number in, recoil equilibrium block 54 spring 57 that is positioned is pressed to ratchet circle 51a one side, shown in solid line among Fig. 9, catch arm 54b combines to ground with ratchet circle 51a folk prescription, foot-on with compared originally, the engine starting is more smooth, the flywheel moment of rotating clutch output shaft 2 when starting before pushing away, by with the ratchet circle 51a of pressure plate 9 all-in-one-piece lobe plates 51 and recoil equilibrium block 54, be passed to clutch input gear 5, import the bent axle that gear 5 is passed to engine again by clutch, the starting of engine just can be carried out more smoothly.
In addition, because after the engine starting, recoil equilibrium block 54 is than ratchet circle 51a revolution in advance, catch arm 54b swings along tooth peak and the tooth paddy of ratchet circle 51a successively, so clutch outer member 52 surpasses winding number that idle running is decided, can determine to make 54 swings of recoil equilibrium block to throw off and the combining of 51a thereby act on centrifugal force on the equilibrium block arm 54a, so just can prevent that catch arm 54b from combining the generation of the unfavorable condition that can not break away from sometimes with the tooth of ratchet circle 51a.
As mentioned above, when clutch outer member 52 reaches winding number more than the winding number that idle running is decided, above-mentioned retaining spring can not block equilibrium block arm 54a swing laterally owing to centrifugal action, shown in the double dot dash line among Fig. 9,54 swings of recoil equilibrium block, catch arm 54b is disengaged with the combining of tooth of ratchet circle 51, so direct transmission of torque path has just been broken off between pressure plate 9 and the clutch outer member 52, they become separate component mutually, and the opposing torque limting mechanism can be brought into play its function freely.
Promptly, with last embodiment similarly, in time when Reduced Speed Now or between vehicle stops, clutch outer member 52 is when winding number more than the winding number that idle running is decided, the combination that is produced by recoil equilibrium block 54 is in the state of being disengaged, bear the opposing torque that comes from the engine break on the clutch, on gyratory directions, go ahead of the rest than pressure plate 9 with clutch output shaft 2 all-in-one-piece clutch core 8 in engine one side as driven shaft, by promote between pin 25 and the cam recess 20 combine and at axial push pressure plate 9, interval between the lip part 8d of it and clutch core 8 just enlarges, thereby weakened frictional engagement, clutch can produce suitable slip, alleviate excessive opposing torque and act on clutch input gear 5, alleviated the load that engine one side is born, thereby the effect that can prevent revolution and engine break is excessive.
Thereby present embodiment also is to make opposing torque limting mechanism and limiter zeroing mechanism and deposit, and the both can bring into play their function fully.
Among the present invention, when the winding number when the winding number of clutch core is idle running was following, limiter zeroing mechanism may command opposing torque limting mechanism was not had an effect, so, no matter be foot-on or push away before starting opposing torque limting mechanism be failure to actuate, the engine starting can be carried out smoothly.During situations such as downshift under steam input opposing torque, the winding number the when winding number of clutch core surpasses idle running can not damage the original revolution of crossing that prevents engine functionally of opposing torque limting mechanism, can prevent also that simultaneously the effect of engine break is excessive.
In addition, when the winding number when the winding number of clutch core is idle running was following, connect mechanism linked up Clutch input shaft and clutch output shaft, and no matter foot-on still pushes away preceding starting, the opposing torque limting mechanism is failure to actuate, and the engine starting can be carried out smoothly.When importing opposing torque because of situations such as downshifts in travelling, winding number when the winding number of clutch output shaft surpasses idle running, above-mentioned connect mechanism is removed and is linked, the opposing torque limting mechanism does not damage its original function, can prevent the revolution of crossing of engine, can prevent also that simultaneously the effect of engine break is excessive.
Claims (5)
1. a vehicle friction clutch comprises clutch core (8), pressure plate (9) and clutch outer member (4);
Clutch core (8) and pressure plate (9) are supported on the clutch output shaft (2);
Clamping has clutch plate (10) and clutch friction plate (11) between clutch core (8) and pressure plate (9), and the distance between clutch core (8) and the pressure plate (9) can be dwindled under the effect of disc spring (12), to carry out the transmission of power of clutch;
Described clutch is provided with cam mechanism (20,25), under the input action of the opposing torque of clutch output shaft side, cam mechanism (20,25) make the relative displacement that produces gyratory directions between clutch core (8) and the pressure plate (9), the distance between above-mentioned clutch core and the above-mentioned pressure plate is enlarged;
It is characterized in that:
Described clutch has ratchet and pawl arrangement (40,42), when the winding number when the winding number of above-mentioned clutch core is idle running is following, above-mentioned cam mechanism (20,25) be failure to actuate, thereby limited relative displacement between above-mentioned clutch core and the above-mentioned pressure plate.
2. clutch as claimed in claim 1 is characterized in that:
Described cam mechanism (20,25) has: cam recess (20b), and its rear side at gyratory directions is darker, then slowly shoals glossily in the front side of gyratory directions; Sell (25) with promoting, it is arranged on the clutch core (8), facing to cam recess (20b),
Described ratchet and pawl arrangement (40,42) has: ratchet plate (40), and it is provided with stop lug boss (40b); With recoil equilibrium block (42), it is provided with stop arm (42b), can joltily with pivotal mounting, and the front end of stop arm (42b) can withstand on the stop lug boss (40b).
3. clutch as claimed in claim 1 is characterized in that: the cardinal extremity of described disc spring (12) is fixed, and free end withstands on a side of pressure plate (9).
4. a vehicle friction clutch comprises clutch core (8), pressure plate (9) and clutch outer member (4);
Clutch core (8) and pressure plate (9) are supported on the clutch output shaft (2);
Clamping has clutch plate (10) and clutch friction plate (11) between clutch core (8) and pressure plate (9), and the distance between clutch core (8) and the pressure plate (9) can be dwindled under the effect of disc spring (12), to carry out the transmission of power of clutch;
Described clutch is provided with cam mechanism (20,25), under the input action of the opposing torque of clutch output shaft side, cam mechanism (20,25) make the relative displacement that produces gyratory directions between clutch core (8) and the pressure plate (9), the distance between above-mentioned clutch core and the above-mentioned pressure plate is enlarged;
It is characterized in that:
Described clutch has the (51a of bindiny mechanism, 54a, 54b), when the winding number when the winding number of above-mentioned clutch core is idle running is following, above-mentioned (the 51a of bindiny mechanism, 54a 54b) can make the opposing torque of clutch output shaft side be delivered to the Clutch input shaft side, and this power transmission relationship also can disconnect.
5. clutch as claimed in claim 4 is characterized in that: and described bindiny mechanism (51a, 54a 54b) have: ratchet circle (51a), and inner circumferential surface is provided with hook tooth; With recoil equilibrium block (54), it is provided with the stop arm, and (54a 54b), can joltily with pivotal mounting, and stop arm (54b) can withstand the tooth of above-mentioned ratchet circle (51a).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP287201/1994 | 1994-10-28 | ||
| JP287201/94 | 1994-10-28 | ||
| JP28720194A JP3378100B2 (en) | 1994-10-28 | 1994-10-28 | Clutch structure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1127333A CN1127333A (en) | 1996-07-24 |
| CN1055751C true CN1055751C (en) | 2000-08-23 |
Family
ID=17714376
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN95117662A Expired - Fee Related CN1055751C (en) | 1994-10-28 | 1995-10-26 | Clutch structure |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP3378100B2 (en) |
| CN (1) | CN1055751C (en) |
Families Citing this family (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005240752A (en) * | 2004-02-27 | 2005-09-08 | Honda Motor Co Ltd | Mounting structure of acg stator |
| CN101526109B (en) * | 2008-03-03 | 2011-02-02 | 西南大学 | Automatic clutch disc type adaptive clutch |
| JP5879094B2 (en) * | 2011-10-27 | 2016-03-08 | 株式会社エフ・シー・シー | Power transmission device |
| JP5272089B1 (en) * | 2012-03-09 | 2013-08-28 | 株式会社エクセディ | Motorcycle clutch device |
| JP5854900B2 (en) * | 2012-03-16 | 2016-02-09 | 株式会社エフ・シー・シー | Power transmission device |
| US8939270B2 (en) * | 2012-04-16 | 2015-01-27 | Gm Global Technology Operations, Llc | Tabbed separation clutch plate |
| JP6226569B2 (en) * | 2013-05-31 | 2017-11-08 | 本田技研工業株式会社 | Motorcycle clutch structure |
| JP5944879B2 (en) | 2013-10-24 | 2016-07-05 | 本田技研工業株式会社 | Vehicle clutch device |
| EP3069034B1 (en) * | 2013-11-13 | 2017-12-13 | Schaeffler Technologies AG & Co. KG | Ramp system for actuating a frictional clutch |
| EP3077703B1 (en) | 2013-12-06 | 2019-11-13 | Schaeffler Technologies AG & Co. KG | Counterbalance and torque transmission device |
| JP6295690B2 (en) | 2014-02-04 | 2018-03-20 | スズキ株式会社 | Clutch with back torque limiter |
| JP6104959B2 (en) * | 2015-02-09 | 2017-03-29 | 本田技研工業株式会社 | Clutch device |
| CN105666190B (en) * | 2016-04-11 | 2018-08-03 | 重庆真测科技股份有限公司 | A kind of work holder |
| JP7217588B2 (en) * | 2018-01-11 | 2023-02-03 | 株式会社エフ・シー・シー | power transmission device |
| CN112901759A (en) * | 2021-02-04 | 2021-06-04 | 哈尔滨东安汽车发动机制造有限公司 | Friction cooling system for actuator of hybrid power transmission device |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5073928A (en) * | 1973-10-31 | 1975-06-18 | ||
| JPS59219525A (en) * | 1983-05-27 | 1984-12-10 | Yamaha Motor Co Ltd | Friction clutch |
-
1994
- 1994-10-28 JP JP28720194A patent/JP3378100B2/en not_active Expired - Fee Related
-
1995
- 1995-10-26 CN CN95117662A patent/CN1055751C/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5073928A (en) * | 1973-10-31 | 1975-06-18 | ||
| JPS59219525A (en) * | 1983-05-27 | 1984-12-10 | Yamaha Motor Co Ltd | Friction clutch |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH08128462A (en) | 1996-05-21 |
| CN1127333A (en) | 1996-07-24 |
| JP3378100B2 (en) | 2003-02-17 |
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