CN1054676C - Stepless speed variator - Google Patents

Stepless speed variator Download PDF

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Publication number
CN1054676C
CN1054676C CN96121858A CN96121858A CN1054676C CN 1054676 C CN1054676 C CN 1054676C CN 96121858 A CN96121858 A CN 96121858A CN 96121858 A CN96121858 A CN 96121858A CN 1054676 C CN1054676 C CN 1054676C
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China
Prior art keywords
cone
main shaft
transmission main
mentioned
supported
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Expired - Fee Related
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CN96121858A
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CN1157381A (en
Inventor
塚田善昭
中村一彦
鹿山博明
斋藤充
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Honda Motor Co Ltd
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Honda Motor Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/0006—Vibration-damping or noise reducing means specially adapted for gearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02086—Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)
  • Transmission Devices (AREA)
  • Vehicle Body Suspensions (AREA)
  • Threshing Machine Elements (AREA)
  • Extrusion Moulding Of Plastics Or The Like (AREA)

Abstract

A continuously variable transmission T comprises a drive face 29 supported on the outer periphery of an input shaft 23; a driven face 30 supported on the outer periphery of an output shaft 22; a plurality of double cones 39 supported on cone holders 31 and 56 and making contact with the two faces 29 and 30; a casing 1, and a torque cam mechanism 33 arranged between the cone holders 31 and 56. The torque cam mechanism 33 comprises a roller 36 arranged at the cone holders 31 and 56; and a guide groove 41 arranged on the inner wall of the casing 1 in such a state to be inclined with an axis and engaged with the roller 36. It can automatically control the change gear ratio of a continuously variable transmission through simple structure.

Description

Stepless speed variator
The present invention relates to a kind of stepless speed variator, this stepless speed variator has the bicone that is made of the 1st cone that contacts with drive surface and the 2nd cone that contacts with driven surface, and it changes gear ratio by the position of the point of contact of change drive surface and driven surface and the 1st cone and the 2nd cone.
For example, Japanese patent gazette discloses a kind of such stepless speed variator special public clear 47-447 number.
Yet so can not automatically change gear ratio according to the travelling state of vehicle, there is the problem of driving operation trouble by carrying out gear ratio control from outside with manually-operable in above-mentioned existing stepless speed variator.In addition, thus when by the travelling state of sensor detected vehicle, when driving executive component control gear ratio with electric control device, have structure complicated again, the problem that cost is high according to this state.
The present invention In view of the foregoing makes, and its purpose is automatically to control with simple structure the gear ratio of stepless speed variator.
In order to achieve the above object, the stepless speed variator of the 1st invention comprises: housing, be supported on the drive surface of transmission main shaft free to rotately, be supported on the driven surface of transmission main shaft free to rotately, the cone retainer that can move freely along transmission main shaft, be supported on the bicone supporting axle of cone retainer along the element of cone that with the transmission main shaft is center line, constitute by the 1st cone with common bottom surface and the 2nd cone, be supported on above-mentioned bicone supporting axle free to rotately, the 1st cone contact drive surface contacts the bicone of driven surface with the 2nd cone, and the torque cam mechanism that moves this cone retainer according to the input torque of cone retainer along the axial direction of transmission main shaft; It is characterized in that: above-mentioned torque cam mechanism comprises: guiding groove and engage with this guiding groove be directed to member, this guiding groove with respect to above-mentioned axis tilt be located between housing and the cone retainer.
The stepless speed variator of the 2nd invention comprises: the drive surface that is supported on transmission main shaft free to rotately, be bearing in the driven surface of transmission main shaft free to rotately, the cone retainer that can move freely along transmission main shaft, be supported on the bicone supporting axle of cone retainer along the element of cone that with the transmission main shaft is center line, constitute by the 1st cone with common bottom surface and the 2nd cone, be supported on above-mentioned bicone supporting axle free to rotately, the 1st cone contact drive surface contacts the bicone of driven surface with the 2nd cone, and the centrifugal mechanism that moves this cone retainer according to the transmission main shaft input speed along the axial direction of transmission main shaft; It is characterized in that: centrifugal mechanism comprises stationary cam face, movable cam face and centrifugal pallet, this stationary cam face is located at the back side of drive surface, can not move along above-mentioned axial direction, this movable cam face be arranged on the stationary cam face the opposite, can move along above-mentioned axial direction with the cone retainer, this centrifugal pallet is configured between two camming surfaces.
The 3rd invention is except that the formation that comprises the 1st invention, also have following feature: it has the centrifugal mechanism that moves this cone retainer according to the input speed of transmission main shaft along the axial direction of transmission main shaft, above-mentioned centrifugal mechanism comprises the stationary cam face, movable cam face and centrifugal pallet, this stationary cam face be located at drive surface back side, can not move along axial direction, this movable cam face be arranged on the stationary cam face the opposite, can move along above-mentioned axial direction with the cone retainer, this centrifugal pallet is configured between two camming surfaces.
Fig. 1 is the longitudinal section of vehicle with the power unit.
Fig. 2 is the major component enlarged view of Fig. 1.
Fig. 3 is the 3-3 line sectional view of Fig. 2.
Fig. 4 is the 4-4 line sectional view of Fig. 2.
Below, with reference to the accompanying drawings embodiments of the invention are described.
Fig. 1～Fig. 4 illustrates one embodiment of the present of invention.
As shown in Figure 1, this power unit P carries on motorcycle, has the housing 1 that wherein contains motor E and stepless speed variator T.Right shell body 4 three parts that housing 1 is divided into central housing 2, is engaged in the left shell 3 of central housing 2 left surfaces and is engaged in central housing 2 right flanks.Bent axle 6 is supported on central housing 2 and left shell 3 by a pair of ball axis hole 5.5, and cylinder block 7 is supported on central housing 2 and left shell 3 too, and piston 8 can be engaged in the cylinder block 7 with being free to slide, and this bent axle 6 is connected in piston 8 by connecting rod 9.
Left end at bent axle 6 is provided with generator 10, and this generator 10 is covered by the generating hood 11 that is engaged in left shell 3 left surfaces.Right-hand member periphery at the bent axle 6 that extends to right shell body 4 inside can be supported with actuation gear 12 with freely relatively rotating, and this actuation gear 12 can engage with bent axle 6 by the automatic centrifugal clutch 13 of being located at bent axle 6 right-hand members.
Together as can be known with reference to Fig. 2, the transmission main shaft 21 of stepless speed variator T comprises: inboard output shaft 22 and sleeve shape input shaft 23, this sleeve shape input shaft 23 can be engaged in the periphery of this output shaft 22 by needle bearing 24 with freely relatively rotating, and the two ends of output shaft 22 are erected between left shell 3 and the right shell body 4.Be fixed with the driven gear 25 that meshes with above-mentioned actuation gear 12 at input shaft 23.Driven gear 25 is made of inboard gear halfbody 26 and outboard gears halfbody 27, in input shaft 23, this outboard gears halfbody 27 is by a plurality of rubber bumpers 28 by splined joint for this inboard gear halfbody 26 ... can engage with this inboard gear halfbody 26 with relatively rotating a little and mesh with above-mentioned actuation gear 12.When being delivered to engine torque when change of input shaft 23 through driven gear 25 from actuation gear 12, can be by above-mentioned buffer 28 ... distortion alleviate the generation of impact.
(De ラ ィ Block Off ェ-ス) 29, and this drive surface 29 has the ring-type contacting part 29 towards radial outside in the periphery splined joint of input shaft 23 drive surface 1, and can be supported with driven surface in the periphery of output shaft 22 (De リ Block Application Off ェ-ス) 30, and this driven surface 30 has the ring-type contacting part 30 towards radially inner side with freely relatively rotating 1
Form cone shape the 1st cone retainer 31 substantially and can relatively rotate and can be bearing in axially slidably the hub portion 30 of driven surface 30 by needle bearing 32 2Periphery.In the lump as can be known, the guiding groove 4 that is formed at right shell body 4 internal faces that stops torque cam mechanism 33 that the 1st cone retainer 31 rotates to be bearing in the cylinder 36 on this pin 34 and to be used for this cylinder 36 is led with respect to housing 1 by the pin 34 that radially is installed in the 1st cone retainer 31 peripheries, by ball bearing 35 with reference to Fig. 3 1Constitute.Guiding groove 4 1The axis L tilt angle alpha of the relative transmission main shaft 21 of direction.
Be formed with a plurality of apertures 31 at the 1st cone retainer 31 1, and across these a plurality of apertures 31 1Set up a plurality of bicone supporting axles 37 ..., on each bicone supporting axle 37, support bicone 39 by needle bearing 38,38 free to rotately.Bicone supporting axle 37 ... the axis L that is configured in transmission main shaft 21 is on the element of cone of center line, at the surface of contact 29 of drive surface 29 1Surface of contact 30 with driven surface 30 1Between cross.Each bicone 39 is made of the 1st cone 40 and the 2nd cone 41 of total bottom surface, the contacting part 29 of the 1st cone 40 contact drive surface 29 1, the 2nd cone 41 contacts the contacting part 30 of driven surface 30 simultaneously 1
Top at the 1st cone retainer 31 that faces toward bent axle 6 has 1 aperture 31 2The flank of tooth that is contained in the driven gear 25 of the 1st cone retainer 31 inside faces toward above-mentioned aperture 31 2, by this aperture 31 2Make actuation gear 12 and driven gear 25 engagements.
Be provided with centrifugal mechanism 51 on the right side of driven gear 25, this centrifugal mechanism 51 endwisely slips the 1st cone retainer 31 by the rotating speed according to input shaft 23 to change the gear ratio of stepless speed variator T, and it is made of sleeve 52, cam member 54 and a plurality of centrifugal pallet 55.This sleeve 52 is fixed on the periphery of input shaft 23, and this cam member 54 can be engaged in the periphery of sleeve 52 by lining 53 with being free to slide, and these a plurality of centrifugal pallets 55 are configured in the stationary cam face 26 that is formed at driven gear 25 inboard gear halfbodies 26 right flanks 1With the movable cam face 54 that is formed at cam member 54 left surfaces 1Between.In the peripheries that the right-hand member of the 1st cone retainer 31 is fixed the 2nd cone bearing support 56 that covers centrifugal mechanisms 51 with pressure ring 57, the interior week of the 2nd cone bearing support 56 is supported on cam member 54 by ball bearing 58.
The 1st cone bearing support 31 moves with the 2nd cone bearing support 56 and constitutes the space that surrounds transmission main shaft 21, and portion contains driven gear 25, drive surface 29 and centrifugal mechanism 51 within it.1 aperture 31 that above-mentioned space faces toward by driven gear 25 flank of tooth 2With supporting bicone 39 ... aperture 31 1Be communicated with the inner space of housing 1.
The collar with the level 59 that is entrenched in above-mentioned sleeve 52 right-hand members is bearing in the right-hand member periphery of output shaft 22 by ball bearing 60, and the right flank of this ball bearing 60 is fixed on the output shaft 22 by cotter 61.The transmission main shaft 21 that output shaft 22 and input shaft 23 constitute is bearing on the right shell body 4 by the ball bearing 62 that is matched with input shaft 23 peripheries.Compression is provided with spring 64 between spring retainer 63 that is supported on above-mentioned ball bearing 62 and the 2nd cone retainer 56, by the spring force of this spring 64 the 2nd cone retainer 56 and the 1st cone retainer 31 is pushed to left.
And, when increasing, the rotating speed of input shaft 23 makes centrifugal pallet 55 by centrifugal force ... move, push two camming surfaces 26 to radial outside 1, 54 1, the elastic force of cam member 54 antagonistic springs 64 and moving right, thus the 2nd cone retainer 56 and the 1st cone retainer 31 that are connected in this cam member 54 by ball bearing 58 are slided to the right.
In splined joint in output shaft 22 left ends, be provided with compression relief cam mechanism 67 between the left end of the right-hand member of fixing output gears 66 and above-mentioned driven surface 30 by cotter 65.As shown in Figure 4, compression relief cam mechanism 67 is at a plurality of recesses 66 that are formed at output gear 66 right-hand members 1With a plurality of recesses 30 that are formed at driven surface 30 left ends 3Between clamping ball 68, belleville spring 69 is housed to apply towards the preload of dextrad pushing driven surface 30 between output gear 66 and driven surface 30.When in effect torque on the driven surface 30 and and output gear 66 between when producing relative rotation, go up in the direction of leaving output gear 66 (dextrad) by compression relief cam mechanism 67 driven surface 30 applied spring force.
Now get back to Fig. 1.Support the 3rd reduction gear 71 at left shell 3 by ball bearing 70 free to rotately, support the left end of output shaft 22 in the 3rd reduction gear 71 by needle bearing 72 and ball bearing 73 coaxially.Support deboost axles 75 at left shell 3 and central housing 2 by a pair of ball bearing 74,74, the 1st reduction gear 76 and the 2nd reduction gear 77 of being located at deboost axle 75 mesh with above-mentioned output gear 66 and the 3rd reduction gear 71 respectively.Be provided with driving sprocket wheel 79 at the axial region front end that protrudes into the 3rd outside reduction gear 71 from left shell 3, on this driving sprocket wheel, be wound with endless chain 78.Therefore, the rotation of output shaft 22 can be passed through output gear 66, the 1 reduction gear the 76, the 2nd reduction gear the 77, the 3rd reduction gear 71, driving sprocket wheel 79 and endless chain 78 and is delivered to driving wheel.
Be located in the oil circuit 4 of right shell body 4 inside 2Be communicated with the oil circuit 22 that connects output shaft 22 inside vertically 1, by from this oil circuit 22 1The oil that supplies to the 1st cone retainer 31 and the 2nd cone retainer 56 inner spaces lubricates the each several part of stepless speed variator T.
The following describes the effect of the embodiment of the invention with said structure.
As shown in Figure 2, drive surface 29 surface of contact of measuring from the axis L of transmission main shaft 21 29 1Distance A be definite value, drive surface 29 contacting parts of measuring from bicone supporting axle 37 29 1Be variable value (B apart from B L, B T).In addition, driven surface 30 contacting parts of measuring from bicone supporting axle 37 30 1Distance C be variable value (C L, C T), from driven surface 30 contacting parts 30 of transmission main shaft 21 axis L mensuration 1Distance D be definite value.
If the rotating speed of drive surface 29 is N DR, the rotating speed of driven surface 30 is N DN, and gear ratio R is defined as R=N DR/ N DN, then gear ratio R can be determined by following formula.
R＝N DR/N DN＝(B/A)×(D/C)
Shown in Fig. 2 first half, because the rotating speed of the driven gear 25 that is driven by actuation gear 12 when motor E slowly runs is low, so act on the centrifugal pallet 55 of centrifugal mechanism 51 ... on centrifugal force also little, the 2nd cone retainer 56 and the 1st cone retainer 31 move to left under the spring force effect of spring 64.When the 1st cone retainer 31 when left moves, the contacting part 29 of drive surface 29 1Move to the underside side of the 1st cone 40 of bicone 39, increasing apart from B is maximum value B L, simultaneously, the contacting part 30 of active surface 30 1Move to the summit side of the 2nd cone 41 of bicone 39, distance C reduces to minimum value C L
At this moment, owing to above-mentioned distance A, D are definite value, when distance B is increased to maximum value B L, distance C reduces to minimum value C LThe time, above-mentioned gear ratio R increases, and speed change is to bottom gear.
On the other hand, shown in Fig. 2 Lower Half, because the rotating speed height of the driven gear 25 that drives by actuation gear 12 during motor E high speed rotating, so act on the centrifugal pallet 55 of centrifugal mechanism 51 ... on centrifugal force also big, the 2nd cone retainer 56 and the centrifugal pallet 55 of the 1st cone retainer 31 by under centrifugal action, moving to radial outside ... effect and the spring force of revolting spring 64 moves to right-hand.When the 1st cone retainer 31 to right-hand when mobile, the contacting part 29 of drive surface 29 1Move to the summit side of the 1st cone 40 of bicone 39, be reduced to minimum value B apart from B T, simultaneously, the contacting part 30 of driven surface 30 1Move to the underside side of the 2nd cone 41 of bicone 39, distance C is increased to maximum value C T
At this moment, owing to above-mentioned distance A, D are definite value, when distance B reduces to minimum value B T, distance C is increased to maximum value C TThe time, above-mentioned gear ratio R reduces, and speed change is to top gear.
And, can between bottom gear and top gear side, infinitely change the gear ratio of stepless speed variator T according to the rotating speed of motor E.And because the control of above-mentioned gear ratio is carried out automatically by centrifugal mechanism 51, so compare with being provided with from the outside of housing 1, can reduce cost and can make stepless speed variator T miniaturization by simplified structure with the occasion of the gear change control device that manually carries out variable speed operation and occasion that the electrical shift control gear is set.
Like this, the rotation of drive surface 29 can be passed through bicone 39 ... be delivered to driven surface 30 with predetermined gear ratio R, and then the rotation of driven surface 30 is delivered to output gear 66 by compression relief cam mechanism 67.At this moment, when because the torque that acts on driven surface 30 makes and output gear 66 between produce relative rotation, then because the effect of compression relief cam mechanism 67, driven surface 30 is endowed the power of leaving output gear 66 directions, the pushing force synergy of this active force and belleville spring 69 produces drive surface 29 contacting parts 29 1The face on the 1st cone 40 of bicone 39 of being crimped on is pressed and with driven surface 30 contacting parts 30 1The face that is crimped on the 2nd cone 41 of bicone 39 is pressed.
Yet, though the active force of above-mentioned compression relief cam mechanism 67 along left to pushing output gear 66 because the left end of output gear 66 is fixed on output shaft 22 left ends by cotter 65, thus above-mentioned left to pushing force be delivered to output shaft 22.In addition, though the power of energizing of above-mentioned compression relief cam mechanism 67 is along right pushing driven surface 30, this pushing force is by bicone 39 ..., drive surface 29, inboard gear halfbody 26, sleeve 52, ball bearing 62, the collar 59, ball bearing 60 and make and sell 61 and be delivered to the right-hand member of output shaft 22 from driven surface 30.
Therefore, compression relief cam mechanism 67 pushes the tension load effect of the load of output gear 66 and driven surface 30 as output shaft 22 along left and right directions, this tension load is offset by the internal stress of output shaft 22, and the racking that adjustment cam mechanism 67 can not occur is delivered to the situation of housing 1.Like this, just there is no need strength reinforcing with housing 1 to the degree that can bear above-mentioned racking, thereby can make stepless speed variator T lightweight.And, because with 67 pairs of drive surface 29 of 1 compression relief cam mechanism and 30 liang of square active forces of driven surface, so, can reduce part number and cost compared with comparing with the energize occasion of (applying active force) of 67 pairs of drive surface 29 of independent compression relief cam mechanism and 30 liang of sides of driven surface respectively.
In addition, when stepless speed variator T carries out speed change, though the 1st cone retainer 31 has the tendency of rotating around transmission main shaft 21 under the transmitting torque counter-force effect of drive surface 29, be bonded on the guiding groove 4 that is formed in the right shell body 4 owing to be supported on the cylinder 36 of the torque cam mechanism 33 of the 1st cone retainer 31 1And stop this transmitting torque counter-force, so the 1st cone retainer 31 does not rotate and can endwisely slip.
Suddenly quicken in travelling and occasion that engine torque is increased severely at vehicle, along with the sharp increase of above-mentioned engine torque, the transmitting torque counter-force that acts on the 1st cone retainer 31 also increases.Its result, as shown in Figure 3, cylinder 36 is crimped on the guiding groove 4 of inclination with load F 1Wall, by this load F at guiding groove 4 1Component F on the direction 1The 1st cone retainer 31 had shift to the tendency in left side (bottom gear side).That is, gear ratio automatically changes to the bottom gear side under the effect of torque cam mechanism 33, brings into play so-called kickdown (キ ッ Off ダ ゥ Application) effect, effectively vehicle is quickened.
And, gear ratio control during above-mentioned kickdown (キ ッ Network ダ ゥ Application), special gear change control device need not be set, but carry out automatically according to the variation of engine torque, so can reduce cost and make stepless speed variator T miniaturization by simplified structure by torque cam mechanism 33.In addition, only need change the guiding groove 4 of torque cam mechanism 33 1Shape, can easily adjust the variation characteristic of gear ratio.
Though the 1st cone retainer 31 of stepless speed variator T and the bottom of the 2nd cone retainer 56 are immersed in the oil of assembling housing 1 bottom, because supporting bicone 39 ... aperture 31 1And the aperture 32 that faces toward of the flank of tooth of driven gear 25 2Than the position height (with reference to Fig. 2) of pasta OL, so do not have a large amount of oil is immersed in the 1st cone bearing support 31 and the 2nd cone retainer 56 from the bottom of housing 1 inner space.In addition, though from connecting the oily path 22 of output shaft 22 inside 1Lubrication oil is supplied with in inner space to the 1st cone retainer 31 and the 2nd cone retainer 56, but because the centrifugal force that rotation produced of driven gear 25 should fly to the outside by the oil bullet, so only keep lubricated required MIN oil in the inner space of the 1st cone retainer 31 and the 2nd cone retainer 56.
Therefore, 25 of driven gears need to stir a spot of oil, unnecessary can be suppressed at inferior limit owing to stirring the oily power loss that produces.And, owing to can stop, stop member so there is no need to be provided with special oil with the 1st cone retainer 31 and 56 pairs of oil of the 2nd cone retainer, can cut down number of parts.
By in the space of the 1st cone retainer 31 and the 2nd cone retainer 56 formations, disposing driven gear 25 as described above, compare with the occasion that this driven gear 25 is configured to outside the above-mentioned space, not only can reduce oil and stir resistance, and because with drive surface 29 and centrifugal mechanism 51 separate configuration the left and right sides at driven gear 25, so can also effectively utilize the volume in above-mentioned space, make stepless speed variator T compactness.
More than embodiments of the invention are had been described in detail, but the present invention can carry out multiple design alteration in the scope of not leaving its aim.
For example, though embodiment's torque cam mechanism 33 is to establish cylinder 36 in the 1st cone retainer 31 1 sides, establish roller trough 4 in housing 1 one sides 1, but its position relation also can be conversely.
As described above, according to the 1st invention, torque cam mechanism comprises guiding groove and is engaged in the member that is directed to of above-mentioned guiding groove, this guiding groove with respect to axis tilt be located at a side in housing and the cone retainer, and this is directed to member and is located at the opposing party in housing and the cone retainer, so, need not manually carry out variable speed operation, also baroque electric control equipment need not be set, can automatically control the gear ratio of stepless speed variator according to the torque that is delivered to the cone retainer.And, by suitably setting the shape of above-mentioned guiding groove, can easily adjust the speed change characteristic.
According to the 2nd invention, centrifugal mechanism comprises stationary cam face, movable cam face and centrifugal pallet, this stationary cam face be located at drive surface back side, can not move along axial direction, this movable cam face be arranged on the stationary cam face the opposite, can move along above-mentioned axial direction with the cone retainer, this centrifugal pallet is configured between two camming surfaces, so, need not manually carry out variable speed operation, also baroque electric control equipment need not be set, can automatically control the gear ratio of stepless speed variator according to the input speed of transmission main shaft.And, can make the axial dimension miniaturization of stepless speed variator by the reasonable Arrangement of centrifugal mechanism.
According to the 3rd invention,, can provide stepless speed variator cheap, that be suitable for vehicle owing to can automatically control the gear ratio of stepless speed variator according to the input speed of torque that is delivered to the cone retainer and transmission main shaft.

Claims (3)

1. stepless speed variator, it comprises housing (1), be supported on the drive surface (29) of transmission main shaft (21) free to rotately, be supported on the driven surface (30) of transmission main shaft (21) free to rotately, the cone retainer (31 that can move freely along transmission main shaft (21), 56), be supported on cone retainer (31 along the element of cone that with transmission main shaft (21) is center line, 56) bicone supporting axle (37), constitute by the 1st cone (40) with common bottom surface and the 2nd cone (41), be supported on above-mentioned bicone supporting axle (37) free to rotately, the 1st cone (40) contacts drive surface (29) and the bicone (39) of the 2nd cone (41) contact driven surface (30), and according to cone retainer (31,56) input torque moves the torque cam mechanism (33) of this cone retainer (31,56) along axis (L) direction of transmission main shaft (21); It is characterized in that: above-mentioned torque cam mechanism (33) comprising: guiding groove (4 1) and with this guiding groove (4 1) engage be directed to member (36), this guiding groove (4 1) be located at obliquely between housing (1) and the cone retainer (31,56) with respect to above-mentioned axis (L).
2. stepless speed variator as claimed in claim 1, it is characterized in that: it comprises according to the input speed of transmission main shaft (21) moves this cone retainer (31 along axis (L) direction of transmission main shaft (21), 56) centrifugal mechanism (51), above-mentioned centrifugal mechanism (51) comprises stationary cam face (26 1), movable cam face (54 1) and centrifugal pallet (55), this stationary cam face (26 1) be located at drive surface (29) back side, can not move this movable cam face (54 along axis (L) direction 1) be arranged on stationary cam face (26 1) the opposite, can move along above-mentioned axis (L) direction, this centrifugal pallet (55) is configured in above-mentioned two camming surfaces (26 1, 54 1) between.
3. stepless speed variator, it has the drive surface (29) that is supported on transmission main shaft (21) free to rotately, be supported on the driven surface (30) of transmission main shaft (21) free to rotately, the cone retainer (31 that can freely rotate along transmission main shaft (21), 56), be supported on cone retainer (31 along the circular cone parent that with transmission main shaft (21) is center line, 56) bicone supporting axle (37), constitute by the 1st cone (40) with common bottom surface and the 2nd cone (41), be supported on above-mentioned bicone supporting axle (37) free to rotately, the 1st cone (40) contact drive surface (29) contacts the bicone (39) of driven surface (30) with the 2nd cone (41), and the centrifugal mechanism (51) that moves this cone retainer (31,56) according to the input speed of transmission main shaft (21) along axis (L) direction of transmission main shaft (21); It is characterized in that: centrifugal mechanism (51) comprises stationary cam face (26 1), movable cam face (54 1) and centrifugal pallet (55), this stationary cam face (26 1) be located at the back side of drive surface (29), can not move this movable cam face (54 along axis (L) direction 1) be arranged on stationary cam face (26 1) the opposite, can move along above-mentioned axis (L) direction together with cone retainer (31,56), this centrifugal pallet (55) is configured in above-mentioned two camming surfaces (26 1, 54 1) between.
CN96121858A 1995-12-28 1996-12-04 Stepless speed variator Expired - Fee Related CN1054676C (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP343324/95 1995-12-28
JP34332495 1995-12-28
JP343324/1995 1995-12-28

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Publication Number Publication Date
CN1157381A CN1157381A (en) 1997-08-20
CN1054676C true CN1054676C (en) 2000-07-19

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KR (1) KR100231018B1 (en)
CN (1) CN1054676C (en)
IT (1) IT1289688B1 (en)
MY (1) MY127629A (en)

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Publication number Priority date Publication date Assignee Title
JP4935964B2 (en) * 2009-12-24 2012-05-23 株式会社村田製作所 Communication terminal

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0645558A1 (en) * 1993-09-23 1995-03-29 Van Doorne's Transmissie B.V. Continuously variable transmission
WO1995033147A1 (en) * 1994-05-31 1995-12-07 Ntn Corporation Friction type non-stage transmission

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0645558A1 (en) * 1993-09-23 1995-03-29 Van Doorne's Transmissie B.V. Continuously variable transmission
WO1995033147A1 (en) * 1994-05-31 1995-12-07 Ntn Corporation Friction type non-stage transmission

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MY127629A (en) 2006-12-29
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IT1289688B1 (en) 1998-10-16
CN1157381A (en) 1997-08-20
KR970046263A (en) 1997-07-26

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