CN1066526C - Stepless gear - Google Patents
Stepless gear Download PDFInfo
- Publication number
- CN1066526C CN1066526C CN97113040A CN97113040A CN1066526C CN 1066526 C CN1066526 C CN 1066526C CN 97113040 A CN97113040 A CN 97113040A CN 97113040 A CN97113040 A CN 97113040A CN 1066526 C CN1066526 C CN 1066526C
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- CN
- China
- Prior art keywords
- taper
- taper seat
- main shaft
- bipyramid
- gear
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
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Abstract
The present invention relates to a continuously variable transmission which is provided with a drive face supported in the outer circumference of an input shaft, a driven face supported in the outer circumference of an output shaft, and a plurality of double cones which are supported in a cone holder via a double cone supporting shaft and are brought into contact with both of the faces. In the double cone supporting shaft inserted into a bottomed supporting hole, which is bored in the cone holder toward the radius directional outside, the radius directional inside end is brought into contact with a needle bearing which supports the cone holder in a boss part in the driven face, so that the double cone supporting shaft can be prevented from coming off from the supporting hole opening end, and can improve the maintain performance.
Description
The present invention relates to stepless speed variator, this speed changer has the bipyramid body that is made of the 1st taper and the 2nd taper, the 1st taper and transmission umbrella body join, the 2nd taper and driven umbrella body join, by changing the connecting point position mutually of transmission umbrella body and driven umbrella body and the 1st taper and the 2nd taper, change gear ratio.
Known stepless speed variator for example has the pattern of the special public clear 47-447 number record of Japanese patent gazette.The stepless speed variator of this kind pattern has the bipyramid body be can be rotated to support on the taper seat, also inserts in the bearing hole that is formed on the taper seat in case the bipyramid body supporting axle that anti-avulsion goes out.In the prior art,, be to adopt anchor clamps that bipyramid body supporting axle is combined on the taper seat, perhaps bipyramid body supporting axle be pressed in the bearing hole of taper seat in order to prevent deviating from of above-mentioned bipyramid body supporting axle.
But, when preventing that with anchor clamps bipyramid body supporting axle from deviating from, because of the needs anchor clamps have increased number of spare parts.When employing is pressed into the method for bipyramid body supporting axle, must extract bipyramid body supporting axle from bearing hole when taking apart, its operation is trouble, is not easy to maintenance.
The present invention makes in view of the above problems, and its purpose is to provide a kind of and does not adopt special bonded block such as anchor clamps and do not reduce maintenance, can prevent the stepless speed variator that bipyramid body supporting axle is deviate from.
To achieve these goals, among the present invention of the present invention program's 1 record, the bipyramid body supporting axle of supporting bipyramid body insert from transmission main shaft one side wear on the taper seat have in the bottom support hole after, by bearing the taper seat is assembled on the transmission main shaft, radial direction the inner of bipyramid body supporting axle joins with above-mentioned bearing and plays the anti-avulsion effect, so, needn't adopt special parts such as anchor clamps to prevent deviating from of bipyramid body supporting axle, also needn't be pressed into bipyramid body supporting axle in the bearing hole and prevent from.
Fig. 1 is the profile diagram of Vehicular power unit.
Fig. 2 be Fig. 1 want portion's enlarged view.
Fig. 3 is the 3-3 line sectional view among Fig. 2.
Fig. 4 is the 4-4 line sectional view among Fig. 2.
Fig. 5 be Fig. 2 want portion's enlarged view.
Below, with reference to the description of drawings embodiments of the invention.
Fig. 1～Fig. 5 is the figure of expression one embodiment of the invention, and Fig. 1 is the profile diagram of Vehicular power unit.Fig. 2 be Fig. 1 want portion's enlarged view.Fig. 3 is the 3-3 line sectional view among Fig. 2.Fig. 4 is the 4-4 line sectional view among Fig. 2.Fig. 5 be Fig. 2 want portion's enlarged view.
As shown in Figure 1, power unit P is contained on the motor bike, has the casing 1 that holds motor E and stepless speed variator T.Casing 1 is divided into three parts, promptly central box 2, be combined in the left box body 3 of central box 2 left surfaces and be combined in the right case 4 of central box 2 right flanks.Bent axle 6 is bearing on central box 2 and the left box body 3 by a pair of ball bearing 5,5, and cylinder block 7 also is bearing on central box 2 and the left box body 3, and bent axle 6 is connected with piston 8 in being entrenched in cylinder block 7 slidably by connecting rod 9.
Left end at bent axle 6 is provided with generator 10, and this generator 10 is lived by the generating hood 11 that is combined in left box body 3 left surfaces is topped.In the right-hand member periphery of the right case 4 inner bent axles 6 that extend, free rotary ground supporting driving gear 12 relatively, and this driving gear 12 can combine with bent axle 6 by the automatic centrifugal clutch 13 that is located at bent axle 6 right-hand members.
From Fig. 1 and Fig. 2 as seen, 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 entrenched in the periphery of input shaft 22 by needle bearing 24 with rotating relatively freely, and the two ends of output shaft 22 are erected between left box body 3 and the right case 4.On input shaft 23, fixing driven gear 25 with above-mentioned driving gear 12 engagements.Driven gear 25 is made of inboard gear halfbody 26 and outboard gears halfbody 27.Inboard gear halfbody 26 splines are combined on the input shaft 23, and outboard gears halfbody 27 is by several rubber dampers 28 ... can be incorporated into a little with the relative rotation on the inboard gear halfbody 26 and and mesh with above-mentioned driving gear 12.When the engine torque that is delivered to input shaft 23 from driving gear 12 process driven gears 25 changes, by above-mentioned rubber damper 28 ... distortion and alleviate impact force.
In conjunction with transmission umbrella body 29, this transmission umbrella body 29 has the annular abutting part 29 towards the radial direction outside at the periphery spline of input shaft 23
1, supporting driven umbrella body 30 rotatably in the periphery of output shaft 22, this driven umbrella body 30 has the annular abutting part 30 towards the radial direction inboard
1
The 1st taper seat 31 that forms virtually conical shape can rotate relatively by needle bearing 32 and can be bearing in the hub portion 30 of driven umbrella body 30 axially slidably
2Periphery.In the lump as can be known with reference to Fig. 3, torque cam mechanism 33 is used to stop the rotation of the 1st taper seat 31 with respect to casing 1, this torque cam mechanism 33 by upright be located at pin 34 on the 1st taper seat 31 peripheral radius directions, by 35 on ball bearing at the roller 36 on this pin 34, be used to guide this roller 36 and be formed on guide groove 4 on right case 4 internal faces
1Constitute.Guide groove 4
1Direction with respect to the axis L tilt alpha angle of transmission main shaft 21.
Setting up several bipyramid body supporting axles 37 ..., these supporting axles 37 ... crosscut is formed on several fenestras 31 on the 1st bevel gear seat 31
1, bipyramid body 39 can be rotated to support on each bipyramid body supporting axle 37 by needle bearing 38,38.Bipyramid body supporting axle 37 ... the axis L that is configured in transmission main shaft 21 is on the element of cone of center line, is transverse in the abutting part 29 of transmission umbrella body 29
1Abutting part 30 with driven umbrella body 30
1Between.Each bipyramid body 39 constitutes the abutting part 29 of transmission umbrella body 29 by the 1st taper 40 and the 2nd taper 41 of total bottom surface
1Be connected on the 1st taper 40 abutting part 30 of driven umbrella body 30
1Be connected on the 2nd taper 41.
As can be seen from Figure 5, support the bearing hole 31 on the 1st taper seat 31 of being formed at of each bipyramid body supporting axle 37
3Be the bottom outlet that has that wears laterally from the radial direction inboard, this bearing hole 31
3The opening end of radial direction inboard facing needle bearing 32, this needle bearing 32 is bearing in hub portion 30 with the driven umbrella body 30 of transmission main shaft 21 one rotation to the 1st taper seat 31
2Periphery.Therefore, at the fenestra 31 that bipyramid body 39 is entrenched in the 1st taper seat 31
1Under the interior state, bipyramid body supporting axle 37 is connected the bearing hole 31 that bipyramid bodies 39 ground insert the 1st taper seat 31
3Opening end, then bipyramid body supporting axle 37 and bipyramid body 39 just are assembled on the 1st taper seat 31.When the 1st taper seat 31 and driven umbrella body 30 are assembled into the periphery of transmission main shaft 21, the radial direction of bipyramid body supporting axle 37 inner with the hub portion 30 that is located at driven umbrella body 30
2Needle bearing 32 butts between periphery and the 1st taper seat 31 can prevent that bipyramid body supporting axle 37 is from bearing hole 31
3Opening end deviate from.
Like this, because bearing hole 31
3Form the bottom outlet that has that wears laterally from the radial direction inboard of the 1st taper seat 31, prevent to insert this bearing hole 31 with needle bearing 32
3In radial direction the inner of bipyramid body supporting axle 37 deviate from, so, do not need special anti-avulsion parts such as anchor clamps, not only can reduce number of spare parts, and with bipyramid body supporting axle 37 is pressed into bearing hole 31
3Method compare, dismounting has easily improved maintenance.
Offered a fenestra 31 on the 1st taper seat 31 tops relative with bent axle 6
2The flank of tooth of driven gear 25 that is contained in the 1st cone seat 31 inside is towards above-mentioned fenestra 31
2, by this fenestra 31
2 Driving 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 makes the 1st taper seat 31 endwisely slip corresponding to input shaft 23 revolution ground, thus the gear ratio of change stepless speed variator T.Centrifugal mechanism 51 is entrenched in cam part 54 and several governor weights 55 of sleeve 52 peripheries slidably by the sleeve 52 that is fixed on input shaft 23 peripheries, by bearing shell 53 ... constitute, this governor weight 55 is configured in stationary cam face 26
1With movable cam face 54
1Between, stationary cam face 26
1Be formed on the right flank of the inboard gear halfbody 26 of driven gear 25, movable cam face 54
1Be formed on the left surface of cam part 54.The periphery of the 2nd taper seat 56 of topped centrifugal mechanism 51 is fixed on the right-hand member of the 1st taper seat 31 by anchor clamps 57, and the interior week of the 2nd taper seat 56 is bearing on the cam part 54 by ball bearing 58.
The 1st taper seat 31 and the 2nd taper seat 56 common spaces that surround transmission main shaft 21 that form, portion is holding driven gear 25, transmission umbrella body 29 and centrifugal mechanism 51 within it.Above-mentioned space is by 1 fenestra 31 that the flank of tooth faced of driven gear 25
2With supporting bipyramid body 39 ... fenestra 31
1Be communicated with the inner space of casing 1.
The band step axle collar 59 that is entrenched in 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 wedge 61.The main shaft 21 that output shaft 22 and input shaft 23 constitute is bearing on the right case 4 by the ball bearing 62 that is entrenched in input shaft 23 peripheries.Be bearing in the spring 64 that is provided with compressive state between spring seat 63 on the ball bearing 62 and the 2nd taper seat 56, the elastic force of this spring 64 is with the 2nd taper seat 56 and the direction pushing left of the 1st taper seat 31.
When the revolution of input shaft 23 increases, governor weight 55 ... under centrifugal action outside radial direction side shifting and push two camming surfaces 26
1, 54
1, the elastic force of cam part 54 antagonistic springs 64 moves to right, and the 2nd taper seat 56 and the 1st taper seat 31 that are connected on this cam part 54 by ball bearing 58 also just slide to right.
Return Fig. 1, the 3rd reduction gear 71 can be rotated to support on the left box body 3 by ball bearing 70, and the left end of output shaft 22 is bearing on the 3rd reduction gear 71 coaxially by needle bearing 72 and ball bearing 73.Deboost axle 75 is bearing on left box body 3 and the central box 2 by a pair of ball bearing 74,74, and the 1st reduction gear 76 and the 2nd reduction gear 77 that are located on the deboost axle 75 mesh with output gear 66 and the 3rd reduction gear 71 respectively.Stretch out in the axial region front end of the 3rd reduction gear 71 of left box body 3 outsides, be provided with the driving sprocket wheel 79 of the endless chain 78 of reeling.Therefore, the rotation of output shaft 22 is passed 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.
Wear the oil circuit 42 of right case 4 inside and the oil circuit 22 that axially connects output shaft 22 inside
1Be communicated with, from oil circuit 22
1Supply to each one of the oil lubrication stepless speed variator T of the 1st taper seat 31 and the 2nd taper seat 56 inner spaces.
The following describes the action of the embodiment of the invention with above-mentioned structure.
As shown in Figure 2, the abutting part 29 from the axis L of transmission main shaft 21 to transmission umbrella body 29
1Distance A be certain value, the abutting part 29 from bipyramid body supporting axle 37 to transmission umbrella body 29
1Be variable value (B apart from B
L, B
T).In addition, the abutting part 30 from bipyramid body supporting axle 37 to driven umbrella body 30
1Distance C be variable value (C
L, C
T), the abutting part 30 from the axis L of transmission main shaft 21 to driven umbrella body 30
1Distance D be certain value.
If the revolution of transmission umbrella body 29 is N
DR, the revolution of driven umbrella body 30 is N
DN, use R=N
DR/ N
DNWhen defining gear ratio R, then gear ratio R is
R=N
DR/N
DN=(B/A)×(D/C)
Shown in the first half of Fig. 2, when motor E low speed rotation, owing to the rotation number of the driven gear 25 that is driven by driving gear 12 is low, so, act on the governor weight 55 of centrifugal mechanism 51 ... on centrifugal force also little, the 2nd taper seat 56 and the 1st taper seat 31 since the elastic force of spring 64 and left direction move.The 1st cone seat 31 move to left to the time, the abutting part 29 of transmission umbrella body 29
1Move to the underside side of the 1st taper 40 of bipyramid body 39, be increased to maximum value B apart from B
L, the abutting part 30 of driven umbrella body 30 of while
1Move to the summit side of the 2nd taper 41 of bipyramid body 39, distance C is reduced to minimum value C
L
At this moment, owing to above-mentioned distance A, D are certain values, when distance B is increased to maximum value B
L, distance C is reduced to minimum value C
LThe time, it is big that above-mentioned gear ratio R becomes, and speed change is a low rate.
On the other hand, shown in the Lower Half of Fig. 2, when motor E high speed rotating, rotation number height owing to the driven gear 25 that is driven by driving gear 12, so, affact the governor weight 55 of centrifugal mechanism 51 ... on centrifugal force also increase governor weight 55 ... under centrifugal action outside radial direction side shifting, the 2nd taper seat 56 and the 1st taper seat 31 are at governor weight 55 ... effect under, the elastic force of antagonistic spring 64 moves to right.When the 1st taper seat 31 moves to right, the abutting part 29 of transmission umbrella body 29
1Move to the summit side of the 1st taper 40 of bipyramid body 39, be reduced to minimum value B apart from B
T, the abutting part 30 of driven umbrella body 30 of while
1Move to the underside side of the 2nd taper 41 of bipyramid body 39, distance C increases to maximum value C
T
At this moment, owing to above-mentioned distance A, D are certain values, when distance B is reduced to minimum value B
T, distance C increases to maximum value C
TThe time, above-mentioned gear ratio R diminishes, and speed change is a flank speed.
Therefore, the gear ratio of stepless speed variator T is infinitely changed between low and the highest corresponding to motor E revolution ground.And the control of above-mentioned gear ratio is carried out automatically by centrifugal mechanism 51, so, with be provided with the situation of manually carrying out the gear change control device of variable speed operation from casing 1 outside or being provided with the electrical shift control gear and compare, its simple structure, with low cost, and can realize the miniaturization of stepless speed variator T.
As mentioned above, the rotation of transmission umbrella body 29 is by bipyramid body 39 ... be delivered to driven umbrella body 30 with predetermined gear ratio, the rotation of this driven umbrella body 30 is delivered to output gear 66 by pressure-regulating device 67 again.At this moment, act on moment on the driven umbrella body 30 make its with output gear 66 between when producing relative rotation, driven umbrella body 30 is pushed by the pressure-regulating device 67 past directions of leaving output gear 66.The elastic force synergy of this pushing force and belleville spring 69 produces the abutting part 29 of transmission umbrella body 29
1Be crimped onto the surface pressure on the 1st taper 40 of bipyramid body 39, and the abutting part 30 of driven umbrella body 30
1Be crimped onto the surface pressure on the 2nd taper 41 of bipyramid body 39.
The pushing force of compression relief cam mechanism 67 is turn left direction pushing of output gear 66, but because the left end of output gear 66 is fixed on the left end of output shaft 22 by wedge 65, so the pushing force of the direction of turning left is delivered to output shaft 22.In addition, toward the right pushing, this pushing force is passed through bipyramid body 39 from driven umbrella body 30 to the pushing force of compression relief cam mechanism 67 driven umbrella body 30 ..., transmission umbrella body 29, inboard gear halfbody 26, sleeve 52, ball bearing 62, the axle collar 59, ball bearing 60 and wedge 61 be delivered to the right-hand member of output shaft 22.
Therefore, compression relief cam mechanism 67 is the tensile load effect of the loading of output gear 66 and the 30 past left and right directions pushings of driven umbrella body as output shaft 22, the internal stress that this tensile load is output axle 22 disappears mutually, and the pushing load of compression relief cam mechanism 67 is not delivered on the casing 1.Like this, need not to make the intensity of casing 1 to be enhanced to the degree that can stand above-mentioned pushing load, can realize the lightweight of stepless speed variator T.And, because with 67 pushing transmission umbrella body 29 and driven umbrella body 30 both sides of a compression relief cam mechanism, so the situation that pushes transmission umbrella body 29 and driven umbrella body 30 with usefulness compression relief cam mechanism is separately respectively compared, and can reduce number of spare parts and reduce cost.
In addition, when stepless speed variator T carries out speed change, the 1st taper seat 31 should rotate around transmission main shaft 21 under the carry-over moment counter-force effect of transmission umbrella body 29, but this carry-over moment counter-force is because of roller 36 that is bearing in the moment cam mechanism 33 on the 1st bevel gear seat 31 and the guide groove 4 that is formed on the right case 4
1Chimeric and be blocked, so the 1st taper seat 31 does not rotate and can slide vertically.
When quickening to make because of anxious that engine torque is anxious when increasing in the vehicle driving, along with the urgency of engine torque increases, the counter-force that acts on the carry-over moment on the 1st taper seat 31 also increases.Its result, as shown in Figure 3, roller 36 is crimped on the guide groove 4 of inclination by load F
1Wall on, the 1st taper seat 31 is by the guide groove 4 of this load F
1The component F of direction
1Left side pushing (low rate side) toward Fig. 2.That is, under the effect of moment cam mechanism 33, gear ratio automatically changes to the low rate side, brings into play so-called kick down (キ ッ Network ダ ゥ Application) effect, and vehicle is quickened.
And, gear ratio control during above-mentioned kick down is because the variation of moment cam mechanism 33 corresponding engine torques and carrying out automatically, simple structure need not to be provided with special gear change control device, so can reduce the cost and realize the miniaturization of stepless speed variator T.As long as make the guide groove 4 of moment cam mechanism 33
1Change in shape, just can easily regulate the variation characteristic of gear ratio.
Though immersing, the 1st taper seat 31 of stepless speed variator T and the bottom of the 2nd taper seat 56 accumulate in the oil of casing 1 bottom, because supporting bipyramid body 39 ... fenestra 31
1And the fenestra that the flank of tooth faced 32 of driven gear 25
2A large amount of oil is higher than pasta OL (see figure 2), so can not immerse the inner space of the 1st taper seat 31 and the 2nd taper seat 56 from casing 1 bottom.In addition, even the oil of lubricated usefulness is from connecting the oil circuit 22 of output shaft 22 inside
1Supply with the inner space of the 1st taper seat 31 and the 2nd taper seat 56, this oil is owing to the rotary centrifugal force of driven gear 25 disperses to the outside, so the inner space of the 1st taper seat 31 and the 2nd taper seat 56 can keep lubricated required minimal oil mass.
Therefore, 25 of driven gears stir a spot of oil, can suppress the power loss that produces because of unnecessary stirring to greatest extent.And, because the 1st taper seat 31 and the 2nd taper seat 56 have stoped oil, so, the special parts that stop oil needn't be set, can reduce number of spare parts.
As mentioned above, by driven gear 25 being configured in the space that surrounds by the 1st taper seat 31 and the 2nd taper seat 56, compare with the situation that this driven gear 25 is configured in outside the above-mentioned space, can not only reduce the stirring resistance of oil, and owing to can be configured in transmission umbrella body 29 and centrifugal mechanism 51 symmetrically the left and right sides of driven gear 25, so effectively utilize the volume in above-mentioned space, make the compact structure of stepless speed variator T.
Describe embodiments of the invention above in detail, but the present invention is not limited to this embodiment, in the scope that does not change main points, the present invention can make various design alterations.
For example, in an embodiment, prevent that the needle bearing 32 that bipyramid body supporting axle 37 is deviate from directly is not configured between the 1st taper seat 31 and the transmission main shaft 21, but the hub portion 30 that the between folder is being established driven umbrella body 30
2, but also can directly be configured in needle bearing 32 between the 1st taper seat 31 and the transmission main shaft 21.That is, needle bearing 32 also can support transmission main shaft 21 directly or indirectly.In addition, also can not use needle bearing 32, and the bearing of other kind of employing ball bearing etc.
As mentioned above, the invention of scheme 1 record, because bipyramid body supporting axle inserts and wears having in the bottom support hole on the taper seat from transmission main shaft one side, prevent from by the bearing that the taper seat is bearing on the transmission main shaft, so, needn't adopt special parts such as anchor clamps to prevent deviating from of bipyramid body supporting axle, also needn't be pressed into bipyramid body supporting axle, like this, can reduce number of spare parts, improve maintenance.
Claims (1)
1. a stepless speed variator has
But the transmission umbrella body (29) of free rotary ground supporting on transmission main shaft (21),
But the driven umbrella body (30) of free rotary ground supporting on transmission main shaft (21),
The taper seat (31,56) that can move freely along transmission main shaft (21),
Be bearing in bipyramid body supporting axle (37) on the taper (31,56) like that along the element of cone that with transmission main shaft (21) is center line,
By the 1st taper (40) of total bottom surface and the 2nd taper (41) but the bipyramid body (39) of free rotary ground supporting on bipyramid body supporting axle (37) of formation, the 1st taper (40) joins with transmission umbrella body (29), the 2nd taper (41) joins with driven umbrella body (30)
Corresponding to the input rotation number of transmission main shaft (21), the centrifugal mechanism (51) that axis (L) direction of taper seat (31,56) in transmission main shaft (21) moved,
It is characterized in that, above-mentioned bipyramid body supporting axle (37) inserts and wears having in the bottom support hole (313) on the taper seat (31,56) from transmission main shaft (21) one sides, is prevented from by the bearing (32) that taper seat (31,56) is supported on the transmission main shaft (21).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP35122596A JPH10184839A (en) | 1996-12-27 | 1996-12-27 | Continuously variable transmission |
| JP351225/96 | 1996-12-27 | ||
| JP351225/1996 | 1996-12-27 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1186186A CN1186186A (en) | 1998-07-01 |
| CN1066526C true CN1066526C (en) | 2001-05-30 |
Family
ID=18415900
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN97113040A Expired - Fee Related CN1066526C (en) | 1996-12-27 | 1997-05-29 | Stepless gear |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JPH10184839A (en) |
| CN (1) | CN1066526C (en) |
| IT (1) | IT1292306B1 (en) |
| TW (1) | TW339397B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101037132B (en) * | 2003-09-29 | 2010-10-06 | 本田技研工业株式会社 | Power unit structure for hybrid vehicle |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5028264B2 (en) * | 2005-09-06 | 2012-09-19 | 株式会社ミクニ | Planetary roller transmission and vehicle equipped with the same |
| US9090312B2 (en) * | 2012-01-12 | 2015-07-28 | Shimano Inc. | Continuously variable bicycle transmission |
| CN108502094B (en) * | 2018-05-14 | 2024-04-02 | 赵宁 | Planetary gear stepless speed change system |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS474417Y1 (en) * | 1967-05-31 | 1972-02-16 | ||
| US5129869A (en) * | 1989-06-23 | 1992-07-14 | Kubota Corporation | Ring cone type stepless transmission |
| CN2186823Y (en) * | 1994-04-11 | 1995-01-04 | 郑州市蝶阀厂 | Self-control conical wheel stageless variator |
| WO1995033147A1 (en) * | 1994-05-31 | 1995-12-07 | Ntn Corporation | Friction type non-stage transmission |
| US5545101A (en) * | 1993-07-20 | 1996-08-13 | Ntn Corporation | Friction type continuously variable transmission |
-
1996
- 1996-12-27 JP JP35122596A patent/JPH10184839A/en active Pending
-
1997
- 1997-04-03 TW TW086104305A patent/TW339397B/en not_active IP Right Cessation
- 1997-05-15 IT IT97TO000409A patent/IT1292306B1/en active IP Right Grant
- 1997-05-29 CN CN97113040A patent/CN1066526C/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS474417Y1 (en) * | 1967-05-31 | 1972-02-16 | ||
| US5129869A (en) * | 1989-06-23 | 1992-07-14 | Kubota Corporation | Ring cone type stepless transmission |
| US5545101A (en) * | 1993-07-20 | 1996-08-13 | Ntn Corporation | Friction type continuously variable transmission |
| CN2186823Y (en) * | 1994-04-11 | 1995-01-04 | 郑州市蝶阀厂 | Self-control conical wheel stageless variator |
| WO1995033147A1 (en) * | 1994-05-31 | 1995-12-07 | Ntn Corporation | Friction type non-stage transmission |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101037132B (en) * | 2003-09-29 | 2010-10-06 | 本田技研工业株式会社 | Power unit structure for hybrid vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| ITTO970409A0 (en) | 1997-05-15 |
| CN1186186A (en) | 1998-07-01 |
| TW339397B (en) | 1998-09-01 |
| JPH10184839A (en) | 1998-07-14 |
| ITTO970409A1 (en) | 1998-11-15 |
| IT1292306B1 (en) | 1999-01-29 |
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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 | ||
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