CN1054674C - Stepless speed variator - Google Patents

Stepless speed variator Download PDF

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Publication number
CN1054674C
CN1054674C CN96121856A CN96121856A CN1054674C CN 1054674 C CN1054674 C CN 1054674C CN 96121856 A CN96121856 A CN 96121856A CN 96121856 A CN96121856 A CN 96121856A CN 1054674 C CN1054674 C CN 1054674C
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CN
China
Prior art keywords
cone
supported
gear
output shaft
driven
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Expired - Fee Related
Application number
CN96121856A
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Chinese (zh)
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CN1157379A (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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Publication date
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Publication of CN1157379A publication Critical patent/CN1157379A/en
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Publication of CN1054674C publication Critical patent/CN1054674C/en
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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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • 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
    • 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
    • F16H2057/02095—Measures for reducing number of parts or components

Abstract

A continuously variable transmission T is provided with 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, plural double cones 39 supported on cone holders 31 to abut on both the faces 29, 30, and one pressure regulating cam mechanism 67 supported on the outer periphery of the output shaft 22. The leftward pressing load generated from the pressure regulating cam mechanism 67 is transmitted to the output shaft 22 through an output gear 66 and a cotter 65, and the rightward pressing load is transmitted to the output shaft 22 through the driven face 30, the double cones 39, the drive face 29, an inside gear half-body 26, a sleeve 52, a ball bearing 62, a collar 59, a ball bearing 60, and a cotter 61.

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 like this stepless speed variator special public clear 47-447 number.
Yet above-mentioned existing stepless speed variator is respectively drive surface and driven surface to be crimped on the bicone with torque cam mechanism separately, so need 2 torque cam mechanism, the problem that exists part number and cost to increase.And, owing to be to bear the load that torque cam mechanism takes place, there is the problem that needs to improve the housing rigidity and weight is increased with housing.
The present invention In view of the foregoing makes, and cuts down part number and cost thereby its purpose is the number that reduces torque cam mechanism, thereby and makes the load of torque cam mechanism generation not be delivered to the housing weight reduction.
In order to achieve the above object, the stepless speed variator of the 1st invention has the drive surface that is supported on 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 the bicone of above-mentioned bicone supporting axle free to rotately, and drive surface be crimped on the 1st cone and driven surface be crimped on the compression relief cam mechanism of the 2nd cone; It is characterized in that: make the compression relief cam mechanism that produces pressure regulation power between above-mentioned drive surface and the 1st cone, the 2nd cone and driven surface with above-mentioned drive surface and driven surface, can not be supported on movably on the single transmission main shaft vertically.
The 2nd invention is except that the formation with the 1st invention, also have following feature: transmission main shaft is made of the output shaft and the input shaft that can relatively rotate and can not be supported on with moving axially this output shaft periphery, on input shaft, drive surface can not be supported with moving axially, and on output shaft, an end of compression relief cam mechanism can not be supported with moving axially.
Fig. 1 is the longitudinal section of vehicle with the power unit.
Fig. 2 be Fig. 1 want portion's enlarged view.
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, and Fig. 1 is the longitudinal section of power train in vehicle application unit, Fig. 2 be Fig. 1 want portion's enlarged view, Fig. 3 is the 3-3 line sectional view of Fig. 2, Fig. 4 is the 4-4 line sectional view of Fig. 2.
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 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 bearing 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 is made of the output shaft 22 and the sleeve shape input shaft 23 of inboard, 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 rubber bumper 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 イ Block Off ェ-ス) 29 in the periphery splined joint of input shaft 23 drive surface, this drive surface 29 has the ring-type contacting part 291 towards radial outside, 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 with reference to Fig. 3, stop the torque cam mechanism 33 of the 1st cone retainer 31 rotations by the pin 34 that radially is installed in the 1st cone retainer 31 peripheries with respect to housing 1, be bearing in cylinder 36 on this pin 34 by ball bearing 35, and be used for the guiding groove 4 that is formed at right shell body 4 internal faces that this cylinder 36 is led 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, at 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 within it, drive surface 29 and centrifugal mechanism 51.1 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 engaged 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 to radial outside, push two camming surfaces 26 1, 54 1Thereby, 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 output shaft 22 left ends, be provided with compression relief cam mechanism 67 between the left end by right-hand member of making and selling 65 output gears of fixing 66 and above-mentioned driven surface 30 in splined joint.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 4, on this driving sprocket wheel 79, be wound with endless chain 78.Therefore, the rotation of output shaft 22 can be delivered to driving wheel by output gear the 66, the 1st reduction gear the 76, the 2nd reduction gear the 77, the 3rd reduction gear 71, driving sprocket wheel 79 and endless chain 78.
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 contacting parts 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, increase to maximum value B apart from 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, because above-mentioned distance A, D is a 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 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, because above-mentioned distance A, D is a 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, 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, if by the torque that acts on driven surface 30 and output gear 66 between produce relative rotation, then 66 directions of leaving produce an active force along driven surface 30 from output gear by compression relief cam mechanism 67, the pushing force synergy of this active force and belleville spring 69 produces drive surface 29 contacting parts 29 1Be crimped on the 1st cone 40 of bicone 39 surface pressure and with driven surface 30 contacting parts 30 1Be crimped on the surface pressure on the 2nd cone 40 of bicone 39.
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 system bolt 65, thus above-mentioned left to pushing force be delivered to output shaft 22.In addition, though the active force of above-mentioned compression relief cam mechanism 67 is along right pushing driven surface 30, but 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 system bolt 61 are 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 occasion of 67 pairs of drive surface 29 of independent compression relief cam mechanism and 30 liang of square active forces 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 Star Network ダ ウ Application) effect, can quicken vehicle effectively.
And the gear ratio control during above-mentioned kickdown need not be provided with special gear change control device, but be carried out automatically according to the variation of engine torque by torque cam mechanism 33, so can reduce cost and make stepless speed variator T miniaturization by simplified structure.In addition, only need to 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 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 configuration driven gear 25 in the space that the 2nd cone retainer 56 of the 1st cone retainer 31 constitutes 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 in the scope of not leaving aim of the present invention, can carry out multiple design alteration.
For example, in an embodiment,, also output shaft 22 can be engaged in the periphery of input shaft 23 though be to cooperate input shaft 23 in the periphery of output shaft 22.
As described above, according to the 1st invention, owing to make the compression relief cam mechanism that produces pressure regulation power between above-mentioned drive surface and the 1st cone, the 2nd cone and driven surface with above-mentioned drive surface and driven surface, can not be supported on movably vertically on the single transmission main shaft, so can drive surface and driven surface two sides all be crimped on the bicone by 1 compression relief cam mechanism, can reduce part number and cost thus.And, owing to the load that compression relief cam mechanism is produced can be offset by the internal pressure of transmission main shaft, thus do not need to support above-mentioned load with housing, thus can make the housing lightweight.
According to the 2nd invention, owing to be to constitute by the output shaft and the input shaft that can relatively rotate and can not be supported on with moving axially this output shaft periphery, on input shaft, can not support drive surface with moving axially, end with compression relief cam mechanism can not be bearing on the output shaft with moving axially simultaneously, so can shorten the axial dimension of transmission main shaft.

Claims (2)

1. stepless speed variator, it comprises: be supported on the drive surface (29) on the transmission main shaft (21) free to rotately; Be supported on the driven surface (30) on the transmission main shaft (21) free to rotately; The cone retainer (31,56) that can move freely along transmission main shaft (21); Be supported in the bicone supporting axle (37) of cone retainer (31,56) like that along the element of cone that with transmission main shaft (21) is center line; Be supported on the bicone (39) on the above-mentioned bicone supporting axle (37) that constitutely by the 1st cone (40) with common bottom surface and the 2nd cone (41), free to rotate; And drive surface (29) is crimped on that the 1st cone (40) goes up and driven surface (30) is crimped on compression relief cam mechanism (67) on the 2nd cone (41); It is characterized in that: make the compression relief cam mechanism (67) that produces pressure regulation power between above-mentioned drive surface (29) and the 1st cone the 40, the 2nd cone (41) and driven surface (30) with above-mentioned drive surface (29) and driven surface (30), can not be supported on movably vertically on the single transmission main shaft (21).
2. stepless speed variator as claimed in claim 1, it is characterized in that: transmission main shaft (21) is made of the output shaft (22) and the input shaft (23) that can relatively rotate and can not be supported on with moving axially this output shaft (22) periphery, on input shaft (23), drive surface (29) can not be supported with moving axially, and on output shaft (22), an end of compression relief cam mechanism (67) can not be supported with moving axially.
CN96121856A 1995-12-28 1996-12-04 Stepless speed variator Expired - Fee Related CN1054674C (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP343323/1995 1995-12-28
JP343323/95 1995-12-28
JP34332395A JP3585617B2 (en) 1995-12-28 1995-12-28 Power unit with continuously variable transmission

Publications (2)

Publication Number Publication Date
CN1157379A CN1157379A (en) 1997-08-20
CN1054674C true CN1054674C (en) 2000-07-19

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CN96121856A Expired - Fee Related CN1054674C (en) 1995-12-28 1996-12-04 Stepless speed variator

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JP (1) JP3585617B2 (en)
KR (1) KR100230063B1 (en)
CN (1) CN1054674C (en)
IT (1) IT1289678B1 (en)
MY (1) MY123768A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
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TWI547409B (en) * 2010-03-03 2016-09-01 福柏克智慧財產有限責任公司 Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor

Families Citing this family (46)

* Cited by examiner, † Cited by third party
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US6551210B2 (en) 2000-10-24 2003-04-22 Motion Technologies, Llc. Continuously variable transmission
US6241636B1 (en) 1997-09-02 2001-06-05 Motion Technologies, Llc Continuously variable transmission
USRE41892E1 (en) 1997-09-02 2010-10-26 Fallbrook Technologies Inc. Continuously variable transmission
JP3853963B2 (en) * 1998-03-20 2006-12-06 本田技研工業株式会社 Power unit
KR100884971B1 (en) 2001-04-26 2009-02-23 모션 테크놀로지즈 엘엘씨 Continuously variable transmission
US7011600B2 (en) 2003-02-28 2006-03-14 Fallbrook Technologies Inc. Continuously variable transmission
US7166052B2 (en) 2003-08-11 2007-01-23 Fallbrook Technologies Inc. Continuously variable planetary gear set
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WO2007029564A1 (en) * 2005-09-06 2007-03-15 Mikuni Corp. Planetary roller transmission and vehicle having the same
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CA2976893C (en) 2005-12-09 2019-03-12 Fallbrook Intellectual Property Company Llc Continuously variable transmission
EP1811202A1 (en) 2005-12-30 2007-07-25 Fallbrook Technologies, Inc. A continuously variable gear transmission
US7882762B2 (en) 2006-01-30 2011-02-08 Fallbrook Technologies Inc. System for manipulating a continuously variable transmission
WO2007106874A2 (en) 2006-03-14 2007-09-20 Autocraft Industries, Inc. Improved wheelchair
CN101506495B (en) 2006-06-26 2011-06-15 瀑溪技术公司 Continuously variable transmission
PL2089642T3 (en) 2006-11-08 2013-09-30 Fallbrook Ip Co Llc Clamping force generator
EP2125469A2 (en) 2007-02-01 2009-12-02 Fallbrook Technologies Inc. System and methods for control of transmission and/or prime mover
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US8641577B2 (en) 2007-06-11 2014-02-04 Fallbrook Intellectual Property Company Llc Continuously variable transmission
CA2692476C (en) 2007-07-05 2017-11-21 Fallbrook Technologies Inc. Continuously variable transmission
US8996263B2 (en) 2007-11-16 2015-03-31 Fallbrook Intellectual Property Company Llc Controller for variable transmission
US8321097B2 (en) 2007-12-21 2012-11-27 Fallbrook Intellectual Property Company Llc Automatic transmissions and methods therefor
CA2716908C (en) 2008-02-29 2017-06-27 Fallbrook Technologies Inc. Continuously and/or infinitely variable transmissions and methods therefor
US8317651B2 (en) 2008-05-07 2012-11-27 Fallbrook Intellectual Property Company Llc Assemblies and methods for clamping force generation
US8535199B2 (en) 2008-06-06 2013-09-17 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
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US8818661B2 (en) 2008-08-05 2014-08-26 Fallbrook Intellectual Property Company Llc Methods for control of transmission and prime mover
US8469856B2 (en) 2008-08-26 2013-06-25 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8167759B2 (en) 2008-10-14 2012-05-01 Fallbrook Technologies Inc. Continuously variable transmission
EP3527848B1 (en) 2009-04-16 2022-01-05 Fallbrook Intellectual Property Company LLC Stator assembly and shifting mechanism for a continuously variable transmission
US8888643B2 (en) 2010-11-10 2014-11-18 Fallbrook Intellectual Property Company Llc Continuously variable transmission
AU2012240435B2 (en) 2011-04-04 2016-04-28 Fallbrook Intellectual Property Company Llc Auxiliary power unit having a continuously variable transmission
KR20140114065A (en) 2012-01-23 2014-09-25 폴브룩 인텔렉츄얼 프로퍼티 컴퍼니 엘엘씨 Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
JP6071309B2 (en) 2012-08-01 2017-02-01 株式会社ミクニ Continuously variable transmission
CN102889370B (en) * 2012-10-09 2015-09-30 重庆齿轮箱有限责任公司 Heavy-load vertical uni-drive gear box gear contacting and coloring adjustment method
WO2014172422A1 (en) 2013-04-19 2014-10-23 Fallbrook Intellectual Property Company Llc Continuously variable transmission
CN105240498A (en) * 2015-09-29 2016-01-13 江苏金源锻造股份有限公司 Infinitely variable speed drive device
US10047861B2 (en) 2016-01-15 2018-08-14 Fallbrook Intellectual Property Company Llc Systems and methods for controlling rollback in continuously variable transmissions
TW201825805A (en) 2016-03-18 2018-07-16 福柏克智慧財產有限責任公司 Stator and stator assembly for continuously variable transmission and method for controlling continuously variable transmission
US10023266B2 (en) 2016-05-11 2018-07-17 Fallbrook Intellectual Property Company Llc Systems and methods for automatic configuration and automatic calibration of continuously variable transmissions and bicycles having continuously variable transmissions
US11215268B2 (en) 2018-11-06 2022-01-04 Fallbrook Intellectual Property Company Llc Continuously variable transmissions, synchronous shifting, twin countershafts and methods for control of same
WO2020176392A1 (en) 2019-02-26 2020-09-03 Fallbrook Intellectual Property Company Llc Reversible variable drives and systems and methods for control in forward and reverse directions

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TWI547409B (en) * 2010-03-03 2016-09-01 福柏克智慧財產有限責任公司 Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor

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MY123768A (en) 2006-06-30
JP3585617B2 (en) 2004-11-04
JPH09177920A (en) 1997-07-11
IT1289678B1 (en) 1998-10-16
KR970046261A (en) 1997-07-26
KR100230063B1 (en) 1999-11-15
CN1157379A (en) 1997-08-20
ITTO960947A1 (en) 1998-05-25
ITTO960947A0 (en) 1996-11-25

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