WO2004055411A1 - Variable-ratio transmission device - Google Patents

Variable-ratio transmission device Download PDF

Info

Publication number
WO2004055411A1
WO2004055411A1 PCT/IT2003/000802 IT0300802W WO2004055411A1 WO 2004055411 A1 WO2004055411 A1 WO 2004055411A1 IT 0300802 W IT0300802 W IT 0300802W WO 2004055411 A1 WO2004055411 A1 WO 2004055411A1
Authority
WO
WIPO (PCT)
Prior art keywords
support
shaft
wheel
assembled
rollers
Prior art date
Application number
PCT/IT2003/000802
Other languages
French (fr)
Inventor
Giuseppe Bausola
Giovanni Contardo
Original Assignee
Giuseppe Bausola
Giovanni Contardo
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Giuseppe Bausola, Giovanni Contardo filed Critical Giuseppe Bausola
Priority to JP2004560184A priority Critical patent/JP2006510858A/en
Priority to AU2003288540A priority patent/AU2003288540A1/en
Priority to US10/538,983 priority patent/US7291081B2/en
Priority to BR0316756-9A priority patent/BR0316756A/en
Priority to CA2510329A priority patent/CA2510329C/en
Priority to EP03780663A priority patent/EP1573227A1/en
Publication of WO2004055411A1 publication Critical patent/WO2004055411A1/en

Links

Classifications

    • 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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • F16H1/321—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear the orbital gear being nutating
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/76—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with an orbital gear having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable

Definitions

  • the present invention refers to the field of motion transmission kinematisms, particularly for vehicles, and deals, more particularly, with a variable-ratio transmission device that operates continuously, comprising a support with a circular series of teeth or rollers that rotates around ' a slanted axis, in order to perform an orbital motion, and meshes with a crown with teeth that are parallel to the axis.
  • the crown can directly actuate a user such as, for example, a velocipede hub or, according to a preferred embodiment of the invention, from its opposite part the crown can ' have a second series of teeth that mesh with a circular series of rollers, in turn assembled on a support with slanted axis that is able to perform an orbital movement, said second support being connected to a user.
  • a user such as, for example, a velocipede hub or, according to a preferred embodiment of the invention, from its opposite part the crown can ' have a second series of teeth that mesh with a circular series of rollers, in turn assembled on a support with slanted axis that is able to perform an orbital movement, said second support being connected to a user.
  • the system provides for means adapted to axially slide said roller supports, in order to continously change the reduction ratio.
  • a transmission device is thereby obtained that is composed of a stepless speed change gear, with a ratio among speeds that is continuously variable within an extremely wide range.
  • stepless speed change gears Different types of transmission are known and comprise stepless speed change gears, but these are systems that are excessively encumbrant and cumbersome and that are adapted only for certain types of vehicles but cannot be assembled, for example, on velocipedes such as bicycles, motorcycles or the like.
  • the present invention belongs to this sector and proposes a' continuously variable-ratio transmission device, as claimed in Claim 1, that can find a wide ' range of applications, also due to the fact that its speed can be' changed within an extremely wide range ' and that, due to its characteristics, is particularly adapted to be used also as applied to velocipedes, such as bicycles, motorcycles, or, made of plastics or other light-weight and sturdy material, to white goods or cutting machines, or the like.
  • the arrangement of the device according to the invention is such as to allow easily inserting it within an hub of a motorcycle wheel.
  • the description that follows refers, only as a mere example, to the specific case of a transmission device for velocipedes such as bicycles or motorcycles, but it is clear that the same inventive idea can be validly applied also to different fields and that the scope is not limited by the specific case as described, but extends to all pieces of equipment and vehicles that adopt this transmission device.
  • FIG. 1 schematically sectionally shows a first embodiment of a transmission device according to the invention
  • FIG. 2 schematically sectionally shows a further preferred embodiment of the transmission device according to the invention.
  • reference 1 points out a fixed shaft, that can for example be the shaft of the driving wheel of a velocipede, on which the transmission device according to the invention is assembled.
  • the shaft 1 is grooved and an hollow shaft 2 is assembled thereon and can axially slide with respect to the shaft 1.
  • the hollow shaft 2 position can be changed for example by means of a ring nut 3 or another known system, for example by means of mechanisms with worm screws, or with electronic circuit control.
  • a pair of hollow shafts 5 and 5' are assembled onto the shaft 2, by interposing bearings, bushings or the like, referenced with 4.
  • the shaft 5 is the motion inlet shaft and in case of a transmission for velocipedes is stiffly connected to a pinion or a toothed crown 6 that is moved by the chain.
  • the hollow shaft 5' instead is connected, as will be described below, to the wheel hub, referenced by number 7.
  • the external surface of the shaft 5 is worked in order to define, at least for a certain length, a cylindrical surface with slanted axis B-B with respect to axis A-A of the support shaft 1.
  • axis B-B of the slanted length describes a tapered sufrace with its vertex on axis A-A.
  • a support 9 is assembled, by interposing bearings or bushings 8, such support 9 being substantially composed of a disk or a wheel that has, perimetrally, a plurality of teeth or rollers 10 whose axis rests on a plane that is parallel with the support 9 plane.
  • the rollers 10 are provided to be engaged with the toothing 11 of a wheel 12 assembled idle on a support 13 that is integral with the wheel hub 7.
  • Bearings or bushings 14 allow the wheel 12 to freely rotate with respect to its own support.
  • a ring 15 is hinged, through a pair of dia etrally opposite pins 16, to the support 9 of the rollers 10. It is therefore possible to rotate the ring 15 relative to the support 9, around a first axis that is substantially parallel to the plane of said support 9.
  • the ring 15 is hinged, through two diametrally opposite pins that are offset by about 90° with respect to pins 16, to an external ring 17 that is part of a free-wheeled device that is integral with the internal surface of the hub 7.
  • the rings 15 and 17 consequently make a sort of cardan joint that allows the support 9 of the rollers 10 to rotate with respect to the ring 11 around a first axis and with respect to the ring 17 around a second axis that is orthogonal with the previous axis.
  • the support 9 can perform an orbital movement, taking in succession the rollers 10 to engage the teeth 11 of the wheel 12.
  • the number of rollers 10 on the support 9 is different from the number of teeth 11 of the wheel 12 that are engaged by the rollers 10.
  • the wheel 12 has, from the opposite part to the toothing 11, a symmetrical toothing 11' that engages a series of rollers assembled on the disk support 9' symmetrical to the support 9 and assembled, by interposing bearings, on a length of the hollow shaft 5' that has a slanted axis.
  • the shaft 5' engages, through a toothing 18, a free wheel 19 that in turn is assembled on a box 20 secured to the hub 7.
  • This latter one is assembled on the shafts 5 and 5' by interposing bearings 21 that allow the hub to freely rotate with respect to the shafts.
  • support 9' is hinged to a ring 15' in turn hinged, according to an axis that is orthogonal to the previous one, to a free-wheel device 17 ' , on the internal surface of the hub 7.
  • connection between free wheel 19 and box 20 occurs by interposing one of more clucth disks 22.
  • the operation is as follows.
  • the support 9 can also angularly rotate around axis A-A together with the hollow shaft 5 and these movements, orbital and angular ones, are independent and can be algebraically summed.
  • the support 9 can perform an angular movement around the axis A-A, in practice rotating around this axis and always engaging with the same roller the toothed wheel 12 that is thereby dragged rotating at the same speed of the shaft 5.
  • the second movement is the orbital one, so that the support 9 assumes a different rotation speed with respect to the eccentric of the shaft 5 and therefore starts “orbiting" by sequentially meshing with the wheel 12, namely with one tooth after the other, like a traditional gear.
  • the wheel 12 is rotated with a reduced angular speed with respect to the angular speed of the hollow shaft 5, with a reduction ratio that changes depending on the ratio between number of support rollers and number of teeth 11, in addition to the axial position of the support 5, by changing which it is possible to change the lever arm length with which the rollers 10 go and mesh the rollers 10 of the toothed wheel 12, thereby changing the reduction ratio.
  • the hub 7 is still and prevents the rings 17 and 15 from rotating, so that the support 9 can only perform an orbital movement, rotating the wheel 12 with a certain reduction ratio.
  • the teeth 11' mesh with the rollers 10' of the support 9'.
  • the free wheel 17' prevents the assembly from rotating backwards, ' so that the support 9' is forced to perform an orbital movement that moves it forward.
  • the hub As soon as the hub starts rotating through the ' free wheel ' 17, it transmits the angular motion ' to the ring 15 and from here to the support 9 of the rollers '10, which starts rotating around axis A-A, with a rotation motion that is summed to the orbital motion and that is transmitted to the wheel 12.
  • the central wheel 12 with toothings 11 and 11' is rotated with two types of meshing, orbital and angular ones, as well as the support 9'.
  • the angular movement is automatically limited by the number of hub revolutions .
  • clutch disks 22 can be used for disengaging the device whtn the vehicle is still, thereby obtaining a transmission device with a ratio that changes continuously and within a very wide range, with compact sizes and adapted for numerous applications, among which vehicles and velocipedes.
  • the transmission device can have a simplified configuration that can be seen in Figure 2, that is lacking the second toothing 11', in addition to the second support 9' and the kinematisms downstream of this one.
  • the central wheel 12 is directly ' connected to the hub 7, that is dragged moving at the beginning only due to the orbital motion of the support 9, to which it is overlapped and then, little by little, is replaced by the angular motion.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)
  • Transmission Devices (AREA)
  • Structure Of Transmissions (AREA)
  • Retarders (AREA)

Abstract

A variable-ratio transmission device is disclosed comprising: a support shaft (1); an hollow shaft (5) rotatingly assembled onto the shaft (1); a support (9) assembled onto the hollow shaft (5) in a rotating way with respect to the shaft around a slanted axis with respect to an axis of the support shaft (1); a plurality of rollers or teeth (10) arranged in a circular series on the support (9); a wheel assembled idle onto the shaft (1), equipped with a front toothing (11) adapted to be engaged by the rollers or teeth (10) assembled on the support (9); a rotation of the hollow shaft (5) subjecting the support (9) to an orbital movement adapted to take the teeth or rollers of the support to engage the toothing of the idle wheel (12); means adapted to establish a connection between the wheel (12) and a user to which motion is transmitted, wherein it provides means adapted to axially slide the support (9) or the wheel (12) with respect to the shaft (1).

Description

VARIABLE-RA 10 TRANSMISSION DEVICE
The present invention refers to the field of motion transmission kinematisms, particularly for vehicles, and deals, more particularly, with a variable-ratio transmission device that operates continuously, comprising a support with a circular series of teeth or rollers that rotates around 'a slanted axis, in order to perform an orbital motion, and meshes with a crown with teeth that are parallel to the axis.
In turn, the crown can directly actuate a user such as, for example, a velocipede hub or, according to a preferred embodiment of the invention, from its opposite part the crown can 'have a second series of teeth that mesh with a circular series of rollers, in turn assembled on a support with slanted axis that is able to perform an orbital movement, said second support being connected to a user.
The system provides for means adapted to axially slide said roller supports, in order to continously change the reduction ratio.
A transmission device is thereby obtained that is composed of a stepless speed change gear, with a ratio among speeds that is continuously variable within an extremely wide range.
As known, it would be highly useful to be able to have available, in vehicles, a transmission with continuously changing ratio, both for a more comfortable and soft driving, and to be able to better exploit the engine characteristics that, as is well known, provides an optimum efficiency for a well defined rotation speed.
Different types of transmission are known and comprise stepless speed change gears, but these are systems that are excessively encumbrant and cumbersome and that are adapted only for certain types of vehicles but cannot be assembled, for example, on velocipedes such as bicycles, motorcycles or the like.
The present invention belongs to this sector and proposes a' continuously variable-ratio transmission device, as claimed in Claim 1, that can find a wide' range of applications, also due to the fact that its speed can be' changed within an extremely wide range 'and that, due to its characteristics, is particularly adapted to be used also as applied to velocipedes, such as bicycles, motorcycles, or, made of plastics or other light-weight and sturdy material, to white goods or cutting machines, or the like.
The arrangement of the device according to the invention is such as to allow easily inserting it within an hub of a motorcycle wheel. The description that follows refers, only as a mere example, to the specific case of a transmission device for velocipedes such as bicycles or motorcycles, but it is clear that the same inventive idea can be validly applied also to different fields and that the scope is not limited by the specific case as described, but extends to all pieces of equipment and vehicles that adopt this transmission device.
The present invention will now be described in detail, as a non-limiting example, with reference to the enclosed drawings, in which:
- Figure 1 schematically sectionally shows a first embodiment of a transmission device according to the invention;
- Figure 2 schematically sectionally shows a further preferred embodiment of the transmission device according to the invention.
With reference to Figure 1, reference 1 points out a fixed shaft, that can for example be the shaft of the driving wheel of a velocipede, on which the transmission device according to the invention is assembled.
The shaft 1 is grooved and an hollow shaft 2 is assembled thereon and can axially slide with respect to the shaft 1.
The hollow shaft 2 position can be changed for example by means of a ring nut 3 or another known system, for example by means of mechanisms with worm screws, or with electronic circuit control.
A pair of hollow shafts 5 and 5' are assembled onto the shaft 2, by interposing bearings, bushings or the like, referenced with 4.
The shaft 5 is the motion inlet shaft and in case of a transmission for velocipedes is stiffly connected to a pinion or a toothed crown 6 that is moved by the chain.
The hollow shaft 5' instead is connected, as will be described below, to the wheel hub, referenced by number 7.
The external surface of the shaft 5 is worked in order to define, at least for a certain length, a cylindrical surface with slanted axis B-B with respect to axis A-A of the support shaft 1.
In practice, following the rotation of the hollow shaft 5 around axis A-A, axis B-B of the slanted length describes a tapered sufrace with its vertex on axis A-A.
On the shaft 5, next to the length with slanted axis, a support 9 is assembled, by interposing bearings or bushings 8, such support 9 being substantially composed of a disk or a wheel that has, perimetrally, a plurality of teeth or rollers 10 whose axis rests on a plane that is parallel with the support 9 plane.
The rollers 10 are provided to be engaged with the toothing 11 of a wheel 12 assembled idle on a support 13 that is integral with the wheel hub 7.
Bearings or bushings 14 allow the wheel 12 to freely rotate with respect to its own support.
A ring 15 is hinged, through a pair of dia etrally opposite pins 16, to the support 9 of the rollers 10. It is therefore possible to rotate the ring 15 relative to the support 9, around a first axis that is substantially parallel to the plane of said support 9.
In turn, the ring 15 is hinged, through two diametrally opposite pins that are offset by about 90° with respect to pins 16, to an external ring 17 that is part of a free-wheeled device that is integral with the internal surface of the hub 7.
The rings 15 and 17 consequently make a sort of cardan joint that allows the support 9 of the rollers 10 to rotate with respect to the ring 11 around a first axis and with respect to the ring 17 around a second axis that is orthogonal with the previous axis.
In practice, due to these chances of movement around two orthogonal axes, the support 9 can perform an orbital movement, taking in succession the rollers 10 to engage the teeth 11 of the wheel 12.
The number of rollers 10 on the support 9 is different from the number of teeth 11 of the wheel 12 that are engaged by the rollers 10.
According to a first embodiment of the invention, the wheel 12 has, from the opposite part to the toothing 11, a symmetrical toothing 11' that engages a series of rollers assembled on the disk support 9' symmetrical to the support 9 and assembled, by interposing bearings, on a length of the hollow shaft 5' that has a slanted axis.
The shaft 5' engages, through a toothing 18, a free wheel 19 that in turn is assembled on a box 20 secured to the hub 7.
This latter one is assembled on the shafts 5 and 5' by interposing bearings 21 that allow the hub to freely rotate with respect to the shafts.
Like support 9, also support 9' is hinged to a ring 15' in turn hinged, according to an axis that is orthogonal to the previous one, to a free-wheel device 17 ' , on the internal surface of the hub 7.
In case of application of the device to motorvehicles, the connection between free wheel 19 and box 20 occurs by interposing one of more clucth disks 22.
The operation is as follows.
Motion from the chain is transmitted to the pinion 6, that in turn rotate the hollow shaft 5.
The consequent rotation of the length with slanted axis for this shaft imparts to the support 9 an orbital movement that takes in succession the rollers 10 to mesh with the teeth 11 of the wheel 12.
The support 9 can also angularly rotate around axis A-A together with the hollow shaft 5 and these movements, orbital and angular ones, are independent and can be algebraically summed.
In practice the support 9 can perform an angular movement around the axis A-A, in practice rotating around this axis and always engaging with the same roller the toothed wheel 12 that is thereby dragged rotating at the same speed of the shaft 5. The second movement is the orbital one, so that the support 9 assumes a different rotation speed with respect to the eccentric of the shaft 5 and therefore starts "orbiting" by sequentially meshing with the wheel 12, namely with one tooth after the other, like a traditional gear.
In this case, with an orbital movement of the support 9, the wheel 12 is rotated with a reduced angular speed with respect to the angular speed of the hollow shaft 5, with a reduction ratio that changes depending on the ratio between number of support rollers and number of teeth 11, in addition to the axial position of the support 5, by changing which it is possible to change the lever arm length with which the rollers 10 go and mesh the rollers 10 of the toothed wheel 12, thereby changing the reduction ratio.
At the beginning of operation, the hub 7 is still and prevents the rings 17 and 15 from rotating, so that the support 9 can only perform an orbital movement, rotating the wheel 12 with a certain reduction ratio.
From the opposite part, the teeth 11' mesh with the rollers 10' of the support 9'. The free wheel 17' prevents the assembly from rotating backwards, 'so that the support 9' is forced to perform an orbital movement that moves it forward.
This movement is transformed into a rotation of the eccentric 5' that can be exploited in order to rotate, through the free wheel 19, the box 20 and with this the hub '7 integral therewith.
As soon as the hub starts rotating through the ' free wheel' 17, it transmits the angular motion 'to the ring 15 and from here to the support 9 of the rollers '10, which starts rotating around axis A-A, with a rotation motion that is summed to the orbital motion and that is transmitted to the wheel 12.
Now, the central wheel 12, with toothings 11 and 11', is rotated with two types of meshing, orbital and angular ones, as well as the support 9'.
The angular movement is automatically limited by the number of hub revolutions .
If necessary, like in case of use on a motorvehicle, clutch disks 22 can be used for disengaging the device whtn the vehicle is still, thereby obtaining a transmission device with a ratio that changes continuously and within a very wide range, with compact sizes and adapted for numerous applications, among which vehicles and velocipedes.
In compliance with a second preferred embodiment of the invention, the transmission device can have a simplified configuration that can be seen in Figure 2, that is lacking the second toothing 11', in addition to the second support 9' and the kinematisms downstream of this one.
In this embodiment, particularly suitable'' for bicycles, the central wheel 12 is directly ' connected to the hub 7, that is dragged moving at the beginning only due to the orbital motion of the support 9, to which it is overlapped and then, little by little, is replaced by the angular motion. '
A skilled person in the art will then be able to provide numerous modifications and variations, that will however have to be deemed all included within the scope of the present invention as claimed in the following Claims .

Claims

1. Variable-ratio transmission device characterised in that it provides at least one support (9) for a circular series of rollers (10), said support being assembled idle on a shaft (5) with slanted axis connected to motor means (6) , a rotation of said shaft (5) with slanted axis making said support (9) perform an orbital movement that takes it to engage a toothed wheel (12) with front toothing (11), said toothed wheel (12) with front toothing (11) being connected to a user, and means (2, 3) being provided adapted to axially slide said at least one support (9), in order to change a reduction ratio.
2. Variable-ratio transmission device according ' to' 'claim 1, characterised in that said toothed wheel (12) 'with front toothing (11) has, on an opposite part to said toothing ' (11) , a second series of teeth or rollers (11') that engage a series of rollers or respectively teeth assembled on a support (9') connected to a user, means (2, 3) being provided adapted to axially slide one or both of said supports (9, 9') in order to change ' a reduction ratio.
3. Variable-ratio transmission device characterised in that it comprises:
• a support shaft (1);
• an hollow shaft (5) rotatingly assembled onto said support shaft (1) ;
• a support (9) assembled onto said hollow shaft (5) in a rotating way with respect to said hollow shaft (5) around a slanted axis with respect to an axis of said support shaft (1) ;
• a plurality of rollers or teeth (10) arranged in a circular series on said support (9) ; • a wheel assembled idle onto said support shaft (1) , equipped with a front toothing (11) adapted to be engaged by said rollers or teeth (10) assembled on said support (9);
• a rotation of said hollow shaft (5) subjecting said support (9) to an orbital movement adapted to take said teeth or rollers (10) of said support (9) to engage said toothing (11) of said idle wheel (12) ;
• means adapted to establish a connection between said wheel (12) and a user to which motion is transmitted, characterised in that it provides means adapted to axially slide said support (9) or said wheel (12) with respect to said support shaft (1) .
4. Transmission device according to claim 3, characterised in that it provides on said toothed wheel (12), from an opposite part to said front toothing (11), a further front toothing (11') that engages the rollers of a second support (9') assembled with its axis slanted on an hollow shaft (5') that is also assembled onto said shaft (1') , said second hollow shaft (5') being connected to a user such as an hub of a velocipede.
5. Transmission device according to claim 4, characterised in that said second hollow shaft (5) is connected through a free wheel to an hub box.
6. Transmission device according to claim 5, characterised in that it provides, on an internal part of the hub, a pair of free wheels (17, 17') to which a pair of rings (15, 15') are respectively hinged, in turn respectively hinged to the supports (9, 9') so that said rings (15, 15') can rotate with respect to said free wheels (17, 17') around a first axis and with respect to said supports (9, 9') around a second axis that is orthogonal with the first axis.
7. Transmission device according to claim β, characterised in that said hollow shafts (5, 5') are rotatingly assembled on a grooved hollow shaft (2) , in turn only slidingly assembled onto said support shaft
(1) •
8. Transmission device according to any one of claims 2 to 7, characterised in that it provides said wheel (12) with double front toothing assembled on a central ring- shaped support (14), in turn assembled onto a support that is integral with the wheel hub.
PCT/IT2003/000802 2002-12-16 2003-12-05 Variable-ratio transmission device WO2004055411A1 (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
JP2004560184A JP2006510858A (en) 2002-12-16 2003-12-05 Variable transmission device
AU2003288540A AU2003288540A1 (en) 2002-12-16 2003-12-05 Variable-ratio transmission device
US10/538,983 US7291081B2 (en) 2002-12-16 2003-12-05 Variable-ratio transmission device
BR0316756-9A BR0316756A (en) 2002-12-16 2003-12-05 Variable Ratio Transmission Device
CA2510329A CA2510329C (en) 2002-12-16 2003-12-05 Variable-ratio transmission device
EP03780663A EP1573227A1 (en) 2002-12-16 2003-12-05 Variable-ratio transmission device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITPC2002A000038 2002-12-16
IT000038A ITPC20020038A1 (en) 2002-12-16 2002-12-16 VARIABLE RATIO TRANSMISSION DEVICE

Publications (1)

Publication Number Publication Date
WO2004055411A1 true WO2004055411A1 (en) 2004-07-01

Family

ID=32587892

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IT2003/000802 WO2004055411A1 (en) 2002-12-16 2003-12-05 Variable-ratio transmission device

Country Status (9)

Country Link
US (1) US7291081B2 (en)
EP (1) EP1573227A1 (en)
JP (1) JP2006510858A (en)
CN (1) CN100485215C (en)
AU (1) AU2003288540A1 (en)
BR (1) BR0316756A (en)
CA (1) CA2510329C (en)
IT (1) ITPC20020038A1 (en)
WO (1) WO2004055411A1 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5149938B2 (en) * 2010-06-11 2013-02-20 株式会社シマノ Bicycle hub with built-in motor
CN107630995A (en) * 2016-07-18 2018-01-26 戎华庆 A kind of swinging rolling Wheel-type continuously variable transmission device
CN108555417A (en) * 2018-06-15 2018-09-21 北京风华工具厂 Flame cutting machine transmission mechanism
US11746853B2 (en) * 2019-11-11 2023-09-05 The Gleason Works Pericyclic transmission

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1771807A (en) * 1929-05-28 1930-07-29 Benjamin A Mitchell Transmission device
US1798269A (en) * 1929-08-22 1931-03-31 Hans E Nietsche Power-transmission apparatus
US1896462A (en) * 1931-08-31 1933-02-07 Hans E Nietsche Power transmission apparatus
GB1069814A (en) * 1964-08-26 1967-05-24 Walter Blazo Variable speed transmission gear
US3895540A (en) * 1972-12-27 1975-07-22 Robert Davidson Speed and/or direction change means
DE2516474B1 (en) * 1975-04-15 1976-09-02 Fickelscher Kurt G PLANETARY GEAR TRANSMISSION
US4266446A (en) * 1979-04-05 1981-05-12 Massey-Ferguson Inc. High torque infinitely variable traction drive transmission
DE4212613A1 (en) * 1992-04-15 1993-10-21 Schmidt Lothar Werner Dipl Ing Three-axis, same-axis gearbox for extremely high step-down and step-up gear ratios with tumbling undulating motion sequences

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3590659A (en) * 1969-12-29 1971-07-06 Arthur M Maroth Nutating speed changing mechanical transmission
US4296647A (en) * 1979-05-30 1981-10-27 Vadetec Corporation Differential transmission drive unit
US5718652A (en) * 1994-10-12 1998-02-17 Coronel; Paul Kay Coronel effect positively infinitely variable rotary motion transmission
US6648786B1 (en) * 1999-09-09 2003-11-18 Oechsler Aktiengesellschaft Gearmotors
US6348021B1 (en) * 1999-12-15 2002-02-19 Alphonse J. Lemanski Variable speed power transmission

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1771807A (en) * 1929-05-28 1930-07-29 Benjamin A Mitchell Transmission device
US1798269A (en) * 1929-08-22 1931-03-31 Hans E Nietsche Power-transmission apparatus
US1896462A (en) * 1931-08-31 1933-02-07 Hans E Nietsche Power transmission apparatus
GB1069814A (en) * 1964-08-26 1967-05-24 Walter Blazo Variable speed transmission gear
US3895540A (en) * 1972-12-27 1975-07-22 Robert Davidson Speed and/or direction change means
DE2516474B1 (en) * 1975-04-15 1976-09-02 Fickelscher Kurt G PLANETARY GEAR TRANSMISSION
US4266446A (en) * 1979-04-05 1981-05-12 Massey-Ferguson Inc. High torque infinitely variable traction drive transmission
DE4212613A1 (en) * 1992-04-15 1993-10-21 Schmidt Lothar Werner Dipl Ing Three-axis, same-axis gearbox for extremely high step-down and step-up gear ratios with tumbling undulating motion sequences

Also Published As

Publication number Publication date
US7291081B2 (en) 2007-11-06
AU2003288540A1 (en) 2004-07-09
CA2510329A1 (en) 2004-07-01
US20060052205A1 (en) 2006-03-09
ITPC20020038A1 (en) 2004-06-17
EP1573227A1 (en) 2005-09-14
BR0316756A (en) 2005-10-25
CN1726359A (en) 2006-01-25
CA2510329C (en) 2011-06-21
CN100485215C (en) 2009-05-06
JP2006510858A (en) 2006-03-30

Similar Documents

Publication Publication Date Title
US4309043A (en) Drive system for bicycles and other apparatus
US5454766A (en) Continuously variable transmission having a double eccentric shaft and a worm gear adjusting mechanism
JP2000006877A (en) Power unit for motor-driven vehicle
JPH1078094A (en) Continuously variable transmission using casing as pulley
JPH01266089A (en) Strong drive for bicycle
US5632702A (en) Continuously variable transmission
JP2000110912A (en) Continuously variable transmission for vehicle
CA2510329C (en) Variable-ratio transmission device
EP1661791A3 (en) Variable steering angle mechanism for vehicle steering control apparatus
CN100411902C (en) Power transmission device for vehicle
JPH07507623A (en) Planetary transmission with two driven shafts
JPS62288749A (en) Gear drive having gear ratio variable in stepless manner
US20040180741A1 (en) Power transmission system
JPH09502242A (en) Variable ratio power transmission device
US1660356A (en) Epicyclic change-speed gear
US7963878B2 (en) Hypocycloidal gear train for varying the speed between two shafts and a bicycle having such a hypocycloidal gear train
JP2001349401A (en) Control mechanism of continuously variable transmission
KR20100076365A (en) Continuously variable transmission of hub type
JP2007024297A (en) Power output device in two-wheeler
JP2003294091A (en) Differential gear transmission
JPH0989055A (en) Gear type continuously variable transmission, gear type continuously variable transmission for automobile and gear type continuously variable transmission for general industrial machine
JP2798607B2 (en) transmission
KR101327332B1 (en) continuously variable transmission of hub type
JP2008143420A (en) Driving mechanism of bicycle
JP2798608B2 (en) transmission

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BY BZ CA CH CN CO CR CU CZ DE DK DM DZ EC EE ES FI GB GD GE GH GM HR HU ID IL IN IS JP KE KG KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NO NZ OM PH PL PT RO RU SC SD SE SG SK SL TJ TM TN TR TT TZ UA UG US UZ VC VN YU ZA ZM ZW

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): GH GM KE LS MW MZ SD SL SZ TZ UG ZM ZW AM AZ BY KG KZ MD RU TJ TM AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LU MC NL PT RO SE SI SK TR BF BJ CF CG CI CM GA GN GQ GW ML MR NE SN TD TG

121 Ep: the epo has been informed by wipo that ep was designated in this application
WWE Wipo information: entry into national phase

Ref document number: 2003780663

Country of ref document: EP

ENP Entry into the national phase

Ref document number: 2006052205

Country of ref document: US

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 10538983

Country of ref document: US

Ref document number: 2004560184

Country of ref document: JP

WWE Wipo information: entry into national phase

Ref document number: 2510329

Country of ref document: CA

Ref document number: 20038A61568

Country of ref document: CN

WWP Wipo information: published in national office

Ref document number: 2003780663

Country of ref document: EP

ENP Entry into the national phase

Ref document number: PI0316756

Country of ref document: BR

WWP Wipo information: published in national office

Ref document number: 10538983

Country of ref document: US