CN1346945A - Stepless speed change device - Google Patents
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- CN1346945A CN1346945A CN 01132890 CN01132890A CN1346945A CN 1346945 A CN1346945 A CN 1346945A CN 01132890 CN01132890 CN 01132890 CN 01132890 A CN01132890 A CN 01132890A CN 1346945 A CN1346945 A CN 1346945A
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Abstract
The invention is to reduce the weight and cost of a pressure regulating cam mechanism, to improve an assembling property, and to make the pressure regulating cam mechanism compact along the radial direction of a transmission shaft in a continuously variable transmission transmitting the speed-variable power to a driven rotary member from a driving rotary member by the movement of a carrier supporting a speed change rotary member kept in frictional contact with the driving rotary member and the driven rotary member. The pressure regulating cam mechanism comprises a projection integrally provided on one of the driven rotary member and an output rotary member 61 and protruded to the other side and a recess provided on the other of the driven rotary member and the output rotary member and storing the tip section of the projection in contact with it.
Description
Technical field
What the present invention relates to a kind of framework by supporting and the speed change revolving part of rotary driving part and driven revolving part rubbing contact moves the stepless speed variator that can carry out the speed change transmission from the rotary driving part to driven revolving part.
Background technique
In the past, such stepless speed variator disclosed opening flat 9-177920 number as the Japanese patent gazette spy.
But, this stepless speed variator output revolving part can be limited to moving of the direction of leaving driven revolving part relative to being bearing in rotatably freely on the transmission shaft simultaneously, between output revolving part and driven revolving part, be provided with compression relief cam mechanism, it is delivered to moment of torsion on the output revolving part from driven revolving part by this compression relief cam mechanism, simultaneously, along with of the relative rotation of driven revolving part, driven revolving part is pressed to framework one side with the output revolving part.
Yet, above-mentioned Japanese patent gazette spy drives disclosed stepless speed variator flat 9-177920 number, by constituting compression relief cam mechanism with the corresponding mutually recess that is provided with respectively in circumferential some places and the mutual corresponding spheroid that is entrenched in paired recess respectively of the driven revolving part and the opposed faces of output revolving part.
Such compression relief cam mechanism need be used to keep the retainer of each spheroid, and cause cost and increase and cause that weight increases, also be easy assembling performance excellence hardly.And because in order to realize cam function, bigger with the diameter design of spheroid of having to is so the size along the radial direction of transmission shaft of compression relief cam mechanism is just bigger.In addition, the problem that also has the generation noise that causes owing to the instability of each spheroid in recess.
Summary of the invention
The present invention is in light of this situation and proposes, its purpose be to provide a kind of can weight reduction and reduce cost and improve easy assembling performance and possess along the stepless speed variator of the compression relief cam mechanism of the radial direction compactness of transmission shaft.
In order to achieve the above object, the stepless speed variator of a first aspect of the present invention comprises: can import power from motor, can be bearing in the transmission shaft on the casing freely rotatably; The rotary driving part that can not be connected with this transmission shaft with the relative rotation; Can be bearing in the driven revolving part on the above-mentioned transmission shaft relatively freely rotatably; The framework that can move along the axis of above-mentioned transmission shaft; Have along with the axis of above-mentioned transmission shaft be center line circular cone bus axis, be bearing in the supporting axle on the said frame; Have with contacted cone shape the 1st friction driving face of above-mentioned rotary driving part and with cone shape the 2nd friction driving face of above-mentioned driven revolving part rubbing contact, the speed change revolving part that can rotate freely and can by above-mentioned support shaft supports axially slidably freely; Above-mentioned driven revolving part is clipped in and said frame between the position, can be relative to being bearing on the above-mentioned transmission shaft freely rotatably and to the confined output revolving part of moving of the direction of leaving above-mentioned driven revolving part; Can carry out the moment of torsion transmission between above-mentioned driven revolving part and the above-mentioned output revolving part and can above-mentioned driven revolving part be pressed to the compression relief cam mechanism of said frame one side according to the relative rotation of above-mentioned driven revolving part and above-mentioned output revolving part, it is characterized in that: above-mentioned compression relief cam mechanism is by being arranged on above one of above-mentioned driven revolving part and above-mentioned output revolving part integratedly, being projected into the teat of opposite side and being arranged on above another of above-mentioned driven revolving part and above-mentioned output revolving part, making it accommodate the front end of above-mentioned teat and the recess that is in contact with it is constituted.
According to this structure, owing to accommodate the recess above another that is arranged on driven revolving part and output revolving part and be in contact with it by the front end that will be darted at driven revolving part and the teat above output one of revolving part integratedly, and formation compression relief cam mechanism, so, with with spheroid between driven revolving part and output the existing form between the revolving part compare, owing to do not need retainer, so can not only reduce cost with weight reduction, improve easy assembling performance, and can also solve the problem of the generation noise that causes owing to the instability of spheroid in recess.And, though, must guarantee to a certain extent along the circumferential teat of transmission shaft and the size of recess in order to realize cam function, but because at radial direction along transmission shaft, can make teat and recess less, so, can make compression relief cam mechanism compactness along the radial direction of transmission shaft.
In addition, a second aspect of the present invention is, on the basis of first aspect, it is characterized in that: in the central authorities of making the bowl-shape driven revolving part that above-mentioned rotary driving part one side is opened wide, be provided with the carrying cylinder cylindraceous portion of can be relatively freely supporting by above-mentioned transmission shaft rotatably integratedly, on above-mentioned output revolving part cylindraceous, be provided with the bearing hole of chimeric bearing between this output revolving part and transmission shaft and make it receive the end of output revolving part one side of above-mentioned carrying cylinder portion, the accepting hole that its diameter is bigger than above-mentioned bearing hole, between bearing hole and accepting hole, between the opposed faces of stepped part that is arranged on the ring-type of output on the revolving part and above-mentioned carrying cylinder portion, constitute above-mentioned compression relief cam mechanism, produce around the belleville spring of above-mentioned carrying cylinder portion above-mentioned driven revolving part is pressed against spring force on above-mentioned the 2nd friction driving face, and be arranged between driven revolving part and the output revolving part.
The structure of the invention of putting down in writing according to such second aspect, not only be provided with compression relief cam mechanism each other, and make driven revolving part and output revolving part vertically near configuration, the compactness that can help stepless speed variator, and it will be installed in the carrying cylinder portion of driven revolving part to the belleville spring that driven revolving part applies preload, can improve easy assembling performance.
Description of drawings
Fig. 1 is the longitudinal sectional view of the power transmission structure between expression motor and the stepless speed variator.
Fig. 2 is the amplification longitudinal sectional view of the stepless speed variator under initial (low) velocity ratio state.
Fig. 3 is the amplification longitudinal sectional view of the stepless speed variator under the high transmission ratio state.
Fig. 4 is the amplification view of the 4-4 line of Fig. 3.
Fig. 5 is the amplification view that is used to illustrate that the 5-5 line along Fig. 2 of compression relief cam mechanism action dissects.
Embodiment
Following foundation one embodiment of the invention shown in the drawings describe form of implementation of the present invention.
Fig. 1～shown in Figure 5 is one embodiment of the invention, Fig. 1 is the longitudinal section of the drive mechanism between expression motor and the stepless speed variator, Fig. 2 is the amplification longitudinal sectional view of the stepless speed variator under the initial velocity ratio state, Fig. 3 is the amplification longitudinal sectional view of the stepless speed variator under the high transmission ratio state, Fig. 4 is the 4-4 line amplification view of Fig. 3, and Fig. 5 is amplification view action, that dissect along the 5-5 line of Fig. 2 that is used to illustrate compression relief cam mechanism.
At first, in Fig. 1, be equipped on the output of the motor E on the vehicles such as motorcycle, be that bent axle 11 from this motor E is delivered to output gear 17 by actuation gear 12, driven gear 13, damping spring 14, automatic centrifugal clutch 15, stepless speed variator 16, with driving wheel---the reduction gear 18 that trailing wheel WR links to each other is meshed with above-mentioned output gear 17.
Above-mentioned actuation gear 12, driven gear 13, damping spring 14 and automatic centrifugal clutch 15 are accommodated in the 1st working room 20 that forms in the casing 19 that the crankcase with above-mentioned motor E is connected, above-mentioned stepless speed variator 16, output gear 17 and reduction gear 18 are accommodated in the 2nd working room 21 that forms in above-mentioned casing 19, the the 1st and the 2nd working room 20,21 is formed in the casing 19 in third side that is arranged at the 19a of wall portion on the casing 19.
In the 1st working room 20, dispose input shaft 22 with axis parallel with bent axle 11, the two end part of input shaft 22 can supported by casing 19 freely rotatably.
As everyone knows, automatic centrifugal clutch 15 is by constituting with the bottom: be connected, can be bearing in rotatably freely simultaneously the input component 23 on the input shaft 22 with above-mentioned driven gear 13 by damping spring 14; The bowl-shape output member 24 that is connected with input shaft 22; Can and can joltily be bearing in some centrifugal weights 25 on the input component 23 with the inner face rubbing contact of this output member 24 Make each centrifugal weight 25 ... have to the spring of removing the trend of moving (figure does not show) with the direction of above-mentioned output member 24 rubbing contact, because power reaches input component 23 from motor E, so when the turn up specified value of input component 23 is above, power is reached output member 24, promptly reaches output shaft 22 from input component 23.
Simultaneously with reference to Fig. 2 and Fig. 3, stepless speed variator 16 possesses: have the transmission shaft 26 with the coaxial axis of above-mentioned input shaft 22; Rotary driving part 27 with this transmission shaft 26 one rotation; Can be bearing in the driven revolving part 28 on the transmission shaft 26 relatively freely rotatably; The framework 29 that can move along the axis of transmission shaft 26; Be bearing in the some supporting axles 30,30 on this framework 29 Respectively by these supporting axles 30,30 ... the speed change revolving part 31,31 of supporting ...
One end liquid of transmission shaft 26 is close and can connect the wall 19a of casing 19 freely rotatably, is projected into the 1st working room 20, can not be connected with input shaft 22 with the relative rotation.Rotary driving part 27 has towards the frictional contact surface 27a in the radial direction outside and makes ring-type, for example, so since with transmission shaft 26 make one can not with transmission shaft 26 relative rotations.In addition, driven revolving part 28 is made to open wide bowl-shape of rotary driving part 27 1 sides and by needle bearing 32 and can be bearing in rotatably relatively freely on the above-mentioned transmission shaft 26, is provided with frictional contact surface 28a towards the radial direction inboard at the open end inner face of this driven revolving part 28.
On the 1st frame half 33, be provided with along it circumferentially every the plurality of windows 37 of equal intervals ... supporting axle 30 ... have along with the axis of transmission shaft 26 be center line circular cone bus axis and cross above-mentioned each window 37 ..., some supporting axles 30 ... two supports on the 1st frame half 33.Each speed change revolving part 31 ... respectively by a pair of needle bearing 38,38 ... energy rotates and can be bearing in these supporting axles 30 axially slidably ... on.
On speed change revolving part 31, be provided with cone shape the 1st friction driving face 40 of the frictional contact surface 27a rubbing contact of rotary driving part 27 and with cone shape the 2nd friction driving face 41 of the frictional contact surface 28a rubbing contact of driven revolving part 28.
In the periphery of the 2nd frame half 34 of framework 29, be fixed with the axle 42 that has with the axis of the orthogonal axe of transmission shaft 26, on this axle 42, can be supported with roller 43 freely rotatably.On the other hand, be fastened with bounding means 44 to the U font that extends with the direction of the parallel axes of transmission shaft 26 at the inner face of casing 19, above-mentioned roller 43 is housed in this bounding means 44 rotationally.Therefore, the 2nd frame half 34, be that framework 29 can move along the axial direction of transmission shaft 26, and can not be connected rotatably on the casing 19 around the axis of transmission shaft 26.
Tighten the coaxial passive screw thread 45 of intrinsic and transmission shaft 26 in the 2nd frame half 34 of framework 29, on this passive screw thread 45, be combined with by ball bearing 56 and can be bearing in driving screw thread 46 on the transmission shaft 26 freely rotatably.
Be equipped with in the outside of casing 19 and have the electric motor 47 axis, freely forward and reverse rotation parallel, between this electric motor 47 and above-mentioned driving screw thread 46, be provided with reducing gear 48 with transmission shaft 26.
This reducing gear 48 is by constituting with the bottom: be arranged on the actuation gear 49 on the output shaft of electric motor 47; The 1st idle pulley 50 that is meshed with this actuation gear 49; The 2nd idle pulley 51 with the 1st idle pulley 50 one; Be fixed on the driven gear 52, the 1 and the 2nd idle pulley 50,51 that drive on the screw thread 46, be meshed and have the axis parallel, can support by the idler shaft 53 that is bearing on the casing 19 rotatably freely with transmission shaft 26 with the 2nd idle pulley 51.
When rotating power reaches when driving screw thread 46 by reducing gear 48 from electric motor 47, because being fixed with the framework 29 that screws the passive screw thread 45 on this driving screw thread 46 can move along the axial direction of transmission shaft 26 and can not be connected rotatably on the casing 19 around the axis of transmission shaft 26, so framework 29 just moves along the axial direction of transmission shaft 26.
Such stepless speed variator 16, suppose: the distance from the point of contact of the frictional contact surface 27a of rotary driving part 27 and the 1st friction driving face 40 to the axis of transmission shaft 26 is A, distance from the point of contact of the frictional contact surface 27a of rotary driving part 27 and the 1st friction driving face 40 to the axis of supporting axle 30 is B, distance from the point of contact of the frictional contact surface 28a of driven revolving part 28 and the 2nd friction driving face 41 to the axis of supporting axle 30 is C, distance from the point of contact of the frictional contact surface 28a of driven revolving part 28 and the 2nd friction driving face 41 to the axis of transmission shaft 26 is D, the rotating speed of hypothesis driven revolving part 27 is NI, the rotating speed of driven revolving part 28 is NO, when hypothesis velocity ratio R is R=NI/NO, have:
R＝NI/NO＝(B/A)×(D/C)
And, drive screw thread 46 rotations when making by electric motor 47 and reducing gear 48, make passive screw thread 45 and framework 29 as shown in Figure 2 when moving near the direction of driven revolving part 28, distance C diminishes when becoming Datong District apart from B, because distance A, D are certain, so it is big that velocity ratio R becomes, be that maximum and distance C are initial (low) velocity ratio under for the state of minimum Fig. 2 at distance B.On the other hand, when making passive screw thread 45 and framework 29, as shown in Figure 3, when the direction of leaving driven revolving part 28 moves, diminishing simultaneously apart from B, distance C becomes big, because distance A, D are certain,, be that minimum and distance C are high transmission ratio under for the state of maximum Fig. 3 at distance B so velocity ratio R diminishes.
Simultaneously with reference to Fig. 4, on the driven gear 52 of above-mentioned reducing gear 48, be equipped with integratedly to the side-prominent spacing teat 54 of passive screw thread 45 1.In addition, on passive screw thread 45, be provided with contacting part 55 integratedly, this contacting part 55 along with passive screw thread 45 near driven gear 52, arrive the position that velocity ratio between rotary driving part 27 and the driven revolving part 28 is high transmission ratio, and contact, engage with above-mentioned spacing teat 54, because spacing teat 54 contacts, engages with the contacting part 55 of the passive screw thread 45 that can not rotate around the axis of transmission shaft 26, so having limited the angle of swing that drives screw thread 46 is the axial internal clearance of framework 29.
Central part making the bowl-shape driven revolving part 28 that opens wide to rotary driving part 27 1 sides is provided with the carrying cylinder 28b of portion cylindraceous, between this 28b of carrying cylinder portion and transmission shaft 26 needle bearing 32 is installed.In addition, driven revolving part 28 is held under the arm and framework 29 between position configuration output revolving part 61 cylindraceous is arranged, on this output revolving part 61, be fixed with output gear 17.
Between above-mentioned output revolving part 61 and transmission shaft 26, angular contact bearing 57 is installed.The outer ring of this angular contact bearing 57 is being held under the arm by the output gear 17 and the back-up ring 58 in the interior week that is installed in output revolving part 61.In addition, coaxially around transmission shaft 26 and be inserted in output gear 17 and transmission shaft 26 between an end of spacer sleeve cylindraceous, be against angular contact bearing 57 inner ring, with the end of driven revolving part 28 opposite sides, the other end of this spacer sleeve 59 is against on the baffle ring 60 that is installed on the transmission shaft 26.Therefore, output revolving part 61 and output gear 17 can be bearing on the transmission shaft 26 freely rotatably to mobile being prevented from of leaving driven revolving part 28 directions.
On output revolving part 61, be provided with bearing hole 62 and accepting hole 63, bearing hole 62 is used for the chimeric angular contact bearing 57 that is installed between this output revolving part 61 and the transmission shaft 26, accepting hole 63 diameters are bigger than above-mentioned bearing hole 62, make it can admit the end of output revolving part 61 1 sides of the 28b of carrying cylinder portion on the driven revolving part 28, between bearing hole 62 and accepting hole 63, on output revolving part 61, be provided with stepped part 64 towards the ring-type of the above-mentioned carrying cylinder 28b of portion one side.
Simultaneously with reference to Fig. 5, between the opposed faces of the stepped part 64 of the 28b of carrying cylinder portion of driven revolving part 28 and output revolving part 61, be provided with compression relief cam mechanism 66, some teats 67 of output revolving part 61 1 sides are gone up, are projected into by this compression relief cam mechanism 66 by the 28b of carrying cylinder portion that is arranged on driven revolving part 28 integratedly ... with on the stepped part 64 that is arranged on output revolving part 61, accommodate above-mentioned each teat 67 ... front end and with it contacted some recesses 68 ... constitute.
On the other hand, between driven revolving part 28 and output revolving part 61, be provided with belleville spring 69 and pad 70 around the 28b of carrying cylinder portion, belleville spring 69 is used to produce the spring force on the 2nd friction driving face 40 that frictional contact surface 28a with driven revolving part 28 is pressed to speed change revolving part 31, applies preload to the direction of leaving output revolving part 61 for driven revolving part 28.
And, when effect on driven revolving part 28 has moment of torsion, with output revolving part 61 between when producing relative rotation, shown in Fig. 5 (a), above-mentioned compression relief cam mechanism 66 makes driven revolving part 28 have trend to the direction motion of leaving output revolving part 61, simultaneously rotating power is passed to output revolving part 61 from driven revolving part 28.This active force and the spring force acting in conjunction that is produced by above-mentioned spring 69 make it produce that frictional contact surface 27a with rotary driving part 27 the face on the 1st friction driving face 40 of being pressed against is pressed and the face that the frictional contact surface 28a of driven revolving part 28 is pressed against on the 2nd friction driving face 41 are pressed.
In addition, on the driven revolving part 28 not effect have moment of torsion, and output revolving part 61 between do not produce under the counterrotating neutral condition, shown in Fig. 5 (b), teat 67 ... with recess 68 ... central part contact, under this state, teat 67 ... at recess 68 ... in be in stable status.
Interior perimembranous in the 1st frame half 33 of framework 29 is equipped with thrust-bearing 71, and this thrust-bearing 71 is installed between the 28b of carrying cylinder portion and framework 29 of driven member 28 in the position of initial velocity ratio.
The other end of transmission shaft 26 can be bearing on the casing 19 freely rotatably by ball bearing 72, and the other end of this transmission shaft 26 is connected with trochoid gear pump---oil pump P.On the other hand, the filter 74 of the bottom in the 2nd working room 21 is installed on the casing 19, be provided with the suction oil duct 73 that connects between filter 74 and the oil pump P on this casing 19, on transmission shaft 26, be provided with the oil leab 75 of importing coaxially from the lubricant oil of oil pump P, and, corresponding with stepless speed variator 16, be provided with to make and inner be connected with oil leab 75 and make the some oil-sucking holes 76 of outer end at the outside of transmission shaft 26 opening ...
In addition, corresponding with the bottom in the 1st working room 20, another filter 77 is installed on casing 19, another oil pump that the lubricant oil that is purified by this filter 77 is not shown by figure is through being arranged on each lubricated portion that supply oil duct 78 on the casing 19 supplies to motor E.
Below the effect of present embodiment is described.Can not be fixed with passive screw thread 45 rotatably with on the framework 29 that casing 19 is connected around the axis of transmission shaft 26, the driving screw thread 46 that can be bearing in rotatably around the axis of transmission shaft 26 on the casing 19 screws on above-mentioned passive screw thread 45, is provided with reducing gear 48 between electric motor 47 that is supported by casing 19 and driving screw thread 46.
Therefore, owing to, drive screw thread 46 rotations along with the action of electric motor 47, so, passive screw thread 45, be that framework 29 just moves along the axial direction of transmission shaft 26, can change the velocity ratio of stepless speed variator 16 freely.And, because bear by casing 19 via the rotation counter-force that speed change revolving part 31 acts on the framework 29 by supporting axle 30, electric motor 47 is not born, so electric motor 47 can produce the power that framework 29 is moved along the axial direction of transmission shaft 26, can realize the miniaturization of electric motor 47, in addition, owing to there is no need to establish the reduction speed ratio of reducing gear 48 very big, therefore can also reduce speed change speed.
In addition, in order to determine the position of the framework 29 under the high transmission ratio state, driven gear 52 constitutes a part that is arranged on electric motor 47 and drives the reducing gear 48 between the screw thread 46, on driven gear 52, be provided with spacing teat 54 integratedly, owing to it is contacted being provided with integratedly on the passive screw thread 45 that is fixed on the framework 29 under high transmission ratio state with above-mentioned spacing teat 54, the contacting part 55 of engaging, so compare with the form that lock screw is fixed on the casing 19, this method needn't be processed casing 19, do not need assembling and so on operation on casing 19 yet, therefore, amount of parts can be reduced, processability and easy assembling performance can also be improved.In addition, owing to also needn't guarantee the rigidity of casing 19 by increasing wall thickness, institute is so that weight reduction.
Have again, because spacing teat 54 and contacting part 55 are to be arranged on integratedly respectively on driven gear 52 and the passive screw thread 45, so, can determine accurately that spacing teat 54 fastens with contacting part 55, the axial position of the framework 29 when contacting.
And, the form that makes the spacing teat of driven gear 52 and lock screw on being fixed in casing 19 contact, engage, the angle of swing of driven gear 52 is limited in the scope of less than 360 degree, and the form that the spacing teat 54 that makes driven gear 52 and the contacting part 55 of passive screw thread 45 contact, engage, can also be according to axial internal clearance by the determined passive screw thread 45 of rotation that drives screw thread 46, the rotating range of above-mentioned driven gear 52 is expanded to more than 360 degree, so can improve the design freedom of reducing gear 48.
In addition, output revolving part 61 driven revolving part 28 is clipped in and framework 29 between the position, can be bearing in rotatably relatively freely on the transmission shaft 26, and to mobile being limited of leaving driven revolving part 28 directions, be arranged on the compression relief cam mechanism 66 between output revolving part 61 and the driven revolving part 28, by being arranged on the driven revolving part 28 integratedly, protruding in some teats 67 of output revolving part 61 1 sides ... with be arranged on the output revolving part 61, take in above-mentioned each teat 67 ... front end and the recess 68 that is in contact with it ... constitute.
Therefore, since with make spheroid and compare between driven revolving part 28 and the output existing compression relief cam mechanism between the revolving part 61, do not need to keep the retainer of spheroid, so can reduce cost and weight reduction, not only improve the easy assembling performance of compression relief cam mechanism 66, and can also solve the problem of the generation noise that causes owing to the instability of spheroid in recess.And, in order to realize cam function, though must guarantee to a certain extent along the circumferential teat 67 of transmission shaft 26 ... with recess 68 ... size, but, because along on the direction of the radial direction of transmission shaft 26, can be with teat 67 ... with recess 68 ... do smaller, so, can make compression relief cam mechanism 66 very compact along the radial direction of transmission shaft 26.
Have again, in the central authorities of making the bowl-shape driven revolving part 28 that rotary driving part 27 1 sides are opened wide, be provided with the carrying cylinder 28b of portion cylindraceous integratedly, on output revolving part 61 cylindraceous, be provided with the bearing hole 62 of chimeric needle bearing 32 between this output revolving part 61 and transmission shaft 26 and for the end of output revolving part 61 1 sides that receive the 28b of carrying cylinder portion and make the diameter accepting hole 63 bigger than bearing hole 62, between bearing hole 62 and accepting hole 63, between the relative face of stepped part 64 that is arranged at the ring-type of output on the revolving part 61 and the above-mentioned carrying cylinder 28b of portion, constitute above-mentioned compression relief cam mechanism 66.Therefore, not only be provided with compression relief cam mechanism 66 each other, and making driven revolving part 28 and output revolving part 61, helping the compactness of stepless speed variator 16 vertically near configuration.
Have again, because produce spring force on the 2nd friction driving face 41 that frictional contact surface 28a with driven revolving part 28 is pressed against speed change revolving part 31 around the belleville spring 69 of the 28b of carrying cylinder portion, and be arranged between driven revolving part 28 and the output revolving part 61, so, above-mentioned belleville spring 69 can be assembled on the 28b of carrying cylinder portion of driven revolving part 28, can improve its easy assembling performance.
More than embodiments of the invention are illustrated, but the present invention is not limited to the foregoing description, does not break away from the scope institute notebook invention of claim, can carry out various changes designs.
As previously discussed, the invention of putting down in writing according to above-mentioned first aspect, with with spheroid between driven revolving part and output revolving part, the existing structure that constitutes pressure-regulating device compares, can reduce cost and weight reduction, not only improve easy assembling performance, can also solve the problem of the generation noise that causes owing to the instability of spheroid in recess.And, can make compression relief cam mechanism compactness along the radial direction of transmission shaft.
In addition, the invention of putting down in writing according to second aspect, owing to make driven revolving part and output revolving part vertically near configuration, the compactness that helps stepless speed variator, and, can be assembled in the carrying cylinder portion of driven revolving part to the belleville spring that driven revolving part applies preload, so, easy assembling performance can be improved.
Claims (2)
1. stepless speed variator comprises: can import power from motor (E), can be bearing in the transmission shaft (26) on the casing (19) freely rotatably; The rotary driving part (27) that can not be connected with this transmission shaft (26) with the relative rotation; Can be bearing in the driven revolving part (28) on the above-mentioned transmission shaft (26) relatively freely rotatably; The framework (29) that can move along the axis of above-mentioned transmission shaft (26); Have along with the axis of above-mentioned transmission shaft (26) be center line circular cone bus axis, be bearing in the supporting axle (30) on the said frame (29); Have with contacted cone shape the 1st friction driving face (40) of above-mentioned rotary driving part (27) and with cone shape the 2nd friction driving face (41) of above-mentioned driven revolving part (28) rubbing contact, the speed change revolving part (31) that can rotate freely and can support by above-mentioned supporting axle (30) axially slidably freely; Above-mentioned driven revolving part (28) is clipped in and said frame (29) between the position, can relative to be bearing in rotatably freely that above-mentioned transmission shaft (26) is gone up and restriction to the output revolving part (61) that moves of the direction of leaving above-mentioned driven revolving part (28); Can carry out the moment of torsion transmission between above-mentioned driven revolving part (28) and the above-mentioned output revolving part (61), and can above-mentioned driven revolving part (28) be pressed to the compression relief cam mechanism (66) of said frame (29) one sides according to the relative rotation of above-mentioned driven revolving part (28) and above-mentioned output revolving part (61), it is characterized in that: above-mentioned compression relief cam mechanism (66) is by being arranged on integratedly above one of above-mentioned driven revolving part (28) and above-mentioned output revolving part (61), be projected into the teat (67) of opposite side and be arranged on above-mentioned driven revolving part (28) and above another of above-mentioned output revolving part (61), accommodate, the recess (68) that contacts the front end of above-mentioned teat (67) constitutes.
2. the stepless speed variator of putting down in writing as claim 1, it is characterized in that: in the central authorities of making the bowl-shape driven revolving part (28) that above-mentioned rotary driving part (27) one sides are opened wide, be provided with the carrying cylinder portion cylindraceous (28b) that to support by above-mentioned transmission shaft (26) rotatably relatively freely integratedly, at the bearing hole (62) that is provided with chimeric bearing (32) between this output revolving part (61) and transmission shaft (26) on the above-mentioned output revolving part cylindraceous (61) with receive the end of output revolving part (61) one sides of above-mentioned carrying cylinder portion (28b), the accepting hole (63) that diameter is bigger than above-mentioned bearing hole (26), between bearing hole (62) and accepting hole (63), between the opposed faces of stepped part (64) that is arranged on the ring-type on the output revolving part (61) and above-mentioned carrying cylinder portion (28b), constitute above-mentioned compression relief cam mechanism (66), produce around the belleville spring (69) of above-mentioned carrying cylinder portion (28b) above-mentioned driven revolving part (28) is pressed against spring force on above-mentioned the 2nd friction driving face (41), and be arranged between driven revolving part (28) and the output revolving part (61).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000299298A JP4511708B2 (en) | 2000-09-29 | 2000-09-29 | Continuously variable transmission |
| JP299298/2000 | 2000-09-29 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1346945A true CN1346945A (en) | 2002-05-01 |
| CN1196874C CN1196874C (en) | 2005-04-13 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 01132890 Expired - Fee Related CN1196874C (en) | 2000-09-29 | 2001-09-12 | Stepless speed change device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4511708B2 (en) |
| CN (1) | CN1196874C (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100417844C (en) * | 2003-07-02 | 2008-09-10 | 本田技研工业株式会社 | Gear shift device of manual transmission |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101720397B (en) * | 2007-04-24 | 2013-01-02 | 福博科技术公司 | Electric traction drives |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4122491Y1 (en) * | 1965-10-01 | 1966-11-10 | ||
| JP3853964B2 (en) * | 1998-03-20 | 2006-12-06 | 本田技研工業株式会社 | Lubrication structure of continuously variable transmission in power unit |
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2000
- 2000-09-29 JP JP2000299298A patent/JP4511708B2/en not_active Expired - Fee Related
-
2001
- 2001-09-12 CN CN 01132890 patent/CN1196874C/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100417844C (en) * | 2003-07-02 | 2008-09-10 | 本田技研工业株式会社 | Gear shift device of manual transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2002106668A (en) | 2002-04-10 |
| CN1196874C (en) | 2005-04-13 |
| JP4511708B2 (en) | 2010-07-28 |
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| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C06 | Publication | ||
| PB01 | Publication | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20050413 Termination date: 20130912 |