DE102011016672A1 - Stepless gearbox for e.g. pedal electric cycle, has frictional bodies whose rotational axis is inclined to main axis and lies tangential or perpendicular to imaginary cylindrical periphery of main axis - Google Patents

Stepless gearbox for e.g. pedal electric cycle, has frictional bodies whose rotational axis is inclined to main axis and lies tangential or perpendicular to imaginary cylindrical periphery of main axis

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Publication number
DE102011016672A1
DE102011016672A1 DE102011016672A DE102011016672A DE102011016672A1 DE 102011016672 A1 DE102011016672 A1 DE 102011016672A1 DE 102011016672 A DE102011016672 A DE 102011016672A DE 102011016672 A DE102011016672 A DE 102011016672A DE 102011016672 A1 DE102011016672 A1 DE 102011016672A1
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DE
Germany
Prior art keywords
main axis
characterized
transmission according
continuously variable
variable transmission
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.)
Withdrawn
Application number
DE102011016672A
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German (de)
Inventor
Anmelder Gleich
Original Assignee
Peter Strauss
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.)
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Publication date
Application filed by Peter Strauss filed Critical Peter Strauss
Priority to DE102011016672A priority Critical patent/DE102011016672A1/en
Publication of DE102011016672A1 publication Critical patent/DE102011016672A1/en
Application status is Withdrawn legal-status Critical

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    • BPERFORMING OPERATIONS; TRANSPORTING
    • B62LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62MRIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M11/00Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels
    • B62M11/04Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio
    • B62M11/14Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears
    • B62M11/16Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears built in, or adjacent to, the ground-wheel hub
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H15/00Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/48Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members with members having orbital motion
    • F16H15/50Gearings providing a continuous range of gear ratios
    • F16H15/52Gearings providing a continuous range of gear ratios in which a member of uniform effective diameter mounted on a shaft may co-operate with different parts of another member

Abstract

The gearbox has expanding clutches (6a, 6b) supported in a gear housing for realizing required input and output side pressure forces, and input and output axes lying collinear to a main axis (20). A rotational axis (3) of frictional bodies (2) is inclined to the main axis and lies tangential or perpendicular to an imaginary cylindrical periphery of the main axis. Each frictional body is mounted axially or radially, where the bodies are rotationally symmetrical to the main axis and have variable radius. A planetary gear (8) is arranged in front of and/or behind a transmission part of the body.

Description

  • The current state of the art knows various, infinitely variable in their ratio gearbox, which operate non-positively or frictionally, also called friction gear or Wälzgetriebe. The drive power is transmitted by circumferential forces, which act between rotationally symmetrical friction bodies under a contact force in the radial direction of rotation of the friction body disposed contact surfaces. The resulting flattening at the Reibkörperberührstellen under the contact force can be calculated according to Hertz or Stribeck and are punctiform or linear. The realized friction gear designs have in common that they realize the stepless change in the ratio by continuously changing the radius of the contact surfaces relative to the Reibkörperrotationsachsen. The friction bodies are essentially conical or spherical. The change in the radius is realized in Kugelreibgetrieben mostly by the tilting of the ball axis of rotation relative to a drive / driven body and Kegelreibgetrieben essentially by the displacement of the friction surface along the cone axis. In this case, depending on the friction coefficient of the friction partner and the circumferential force to be transmitted high contact forces necessary, which burden the friction body. These are z. B. by so-called Spreizkupplungen (see DE 41 27 030 A1 ) generated.
  • The indicated in claim 1 invention is based on the problem that, depending on the construction or by the maximum friction material from the Reibkörpermaterial Hertzian pressure, the transmission range of the friction gear is limited.
  • An example of the constructive restriction of the range of transmission is the gearbox of Fallbrook ( WO 2009/111328 A1 ), in which by the axial bearing of the friction balls of the tilt angle whose bearing axes and thus the maximum possible transmission ratio of the transmission is geometrically limited.
  • In conical friction gearboxes, the Hertzian pressure, which grows quadratically with the reduction of the bevel radius, limits a large transmission range, at least in the case of a small design.
  • This problem is solved by the geometric position of the axis of rotation shown in claim 1 (US Pat. 1 ) around which the friction body ( 2 ) can be tilted, solved. In this arrangement, it is possible by tilting the Reibkörperrotationsachse ( 3 ), the ratio of small radius (r) on the drive side (drive side) to large radius (R) on the output side (drive side) and thus theoretically let go the ratio to infinity or to zero (R / r = ∞ or r / R = 0). In doing so, the radius to be used for the calculation of the Hertzian pressure does not change. He remains because of the spherical shape of the friction body always the same size. The theoretically largest possible over- or reduction of the transmission is only limited by the occurring in the friction surface and the efficiency and the maximum sustainable Hertzian pressure determining Bohrmoment.
  • Due to the arrangement shown in claim 1, a bearing of the friction body in the interior is necessary, which separated according to claim 2 axially ( 4 ) and radial ( 5 ) with respect to the Reibkörperrotationsachse is executed. Here are the two types of storage with balls (axial) or needles (radial) to be understood only as an example. It can be used depending on load case and required speed and other Wälzkörperformen, such. B. rolls or tons. The axial bearing serves in this case essentially to support the by the symmetrically mounted Spreizkupplungen ( 6 ) introduced pressing forces, which depending on the tilt angle of Reibkörperrotationsachse ( 3 ) have a resulting, relative to the Reibkörperrotationsachse variable, radial and axial portion. The additional radial bearing serves to stabilize the friction body against the contact forces of the Spreizkupplungen, reduces deformation of the same and thereby increases the overall efficiency of the transmission. In addition, by the radial bearing on the Reibköper ( 2 ) acting circumferential forces.
  • The indicated in claim 3 invention is based on the problem that the circumferential force to be transmitted to the friction body increases with the transmission power under otherwise identical conditions. The problem is solved in that a variable number of friction bodies rotationally symmetrical to the main axis ( 20 ) of the transmission can be arranged and the transmission is thus scalable in terms of power transmission. That is, the circumferential force to be transmitted can be distributed to a plurality of friction bodies.
  • The indicated in claim 4 invention is based on the problem that the maximum sustainable Hertzian pressure of the Reibkörpermaterials, usually steel, is limited. The problem is solved in that the friction radius underlying the Hertzian pressure calculation can be varied. The Hertzian pressure behaves inversely proportional to R 2 . The transmission thus receives another degree of freedom of scalability and thus the ability to adapt to a variety of speed / torque requirements.
  • The indicated in claim 5 invention is based on the problem that a friction gear decisively determining sizes are the Hertzian pressure generated by the required contact force and the occurring in the Hertz contact surface Bohrmoment. Since the required contact force depends, inter alia, directly on the circumferential force to be transmitted and thus indirectly on the input torque or output torque to be transmitted, it is possible to use a planetary gearset (or 8th ) adjust the required input or output torque on the friction gear part. That is, when a high input torque is to be transmitted, a high speed planetary gearset reduces the required torque at the friction gear input and thus the necessary contact force, hertzian pressure and torque. A downstream, slow-speed planetary gear set thus reduces the required torque at the friction gear output. Although this illuminates only a partial aspect of the complex design of the friction gear, it provides a further degree of freedom for a compact design and high efficiency. In addition, the illustrated in claim 1 large translation range of Reibradgetriebes is maintained.
  • The indicated in claim 6 invention is based on the problem to realize a simple, accurate and mutually identical setting of the required translation by tilting each individual friction body. This problem is solved by the one in the ring carrier ( 9 ) Axially immovably mounted worm wheel ( 10 ) by rotation all Reibkörperträger simultaneously tilted. This is done by a gearing ( 11 ) at the foot of Reibkörperträgers ( 12 ) realized in which the worm wheel engages. By this arrangement, an angular adjustment of all friction body is realized to each other, since this is geometrically defined by the pitch of the worm wheel.
  • The specified in claim 7 invention is based on the problem of driving the worm wheel from the outside. This problem is solved in that a hollow shaft leading into the interior of the transmission ( 13 ) a with her rotatably and axially displaceably mounted wing coupling ( 14 ) drives rotationally. This in turn accesses via a radially mounted wing ( 14a ) in a groove of the worm wheel ( 10a ), in order to transmit circumferential forces to a respective flank of the worm wheel on each outer spherical contact surface of the blade. In the axial direction, the wing coupling by a retaining ring ( 15 ) held in the worm wheel. A introduced by manufacturing tolerances radial clearance between the worm wheel and wing coupling is compensated by sliding the spherical bearing surfaces of the wing in the groove flanks of the worm wheel.
  • The specified in claim 8 invention is based on the problem to support the acting on the Reibkörperberührflächen by the circumferential forces around the main axis torque. The problem is solved by that the friction body ( 2 ) carrying friction body carrier ( 12 ) in a gap of the ring carrier ( 9 ) is guided and thus passes on the flanks of the gap, the torque to the ring carrier, which in turn on a hollow shaft leading to the outside ( 16 ) is rotatably mounted.
  • The specified in claim 9 invention is based on the problem that by the Spreizkupplungen ( 6 ) generated in the main axis direction by inertia of the torque transmission processes in the interior of the transmission and by deformation of the components involved can lead to an axial load of the friction body bearing. The problem is solved in that the ring carrier carrying the friction bodies is mounted axially displaceably on the hollow shaft and thus can avoid the friction bodies loaded axially on the transmission input (transmission output) by the expansion coupling in the direction of the expansion coupling on the transmission output (transmission input). That is, there may be a frictional connection between the two Spreizkupplungen, which in turn are supported on the transmission housing.
  • The indicated in claim 10 invention is based on the problem that it is important in the proposed construction that all friction are evenly loaded, otherwise the entire gearbox could fail due to premature wear of an overloaded friction body. An uneven load could be caused inter alia by the axial offset of the Spreizkupplungachse relative to the ring carrier axis.
  • The problem is solved in that the Spreizkupplung by a driving ring ( 17 ), which is not firmly connected to it. The Spreizkupplung engages only by her radially mounted cylindrical pins ( 18 ) in slots ( 17s ) of the driving ring, whereby it receives a radial clearance and can thus center on the friction bodies. This ensures a uniform load of all friction and thus a reduction in the probability of failure by overloading a friction body.
  • QUOTES INCLUDE IN THE DESCRIPTION
  • This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.
  • Cited patent literature
    • DE 4127030 A1 [0001]
    • WO 2009/111328 A1 [0003]

Claims (10)

  1. Continuously variable transmission for rotatably driven vehicles, machinery and equipment, especially for bicycles, pedelecs, mopeds and motorcycles with spherical, the driving force frictionally, by means of a Reibradöles transmitting friction bodies, the respectively required on the input and output side contact pressure is realized by Spreizkupplungen which supported in the gear housing and the input / output axis are each collinear on a main axis, characterized in that the Reibkörperrotationsachse can be tilted about a rotational axis which is tangent to an imaginary peripheral cylinder of the main axis and perpendicular to this.
  2. Continuously variable transmission according to claim 1, characterized in that each Reibköper is mounted axially and radially inside.
  3. Continuously variable transmission according to claim 1, characterized in that a plurality of friction bodies can be arranged rotationally symmetrical to the main axis.
  4. Stepless transmission according to claim 1, characterized in that the Reibkörperradius can be varied.
  5. Continuously variable transmission according to claim 1, characterized in that a planetary gear is arranged before and / or after the Reibkörpergetriebeteil.
  6. Continuously variable transmission according to claim 1, characterized in that the angular displacement of the Reibkörperrotationsachse is effected by a worm wheel mounted in the ring carrier.
  7. Continuously variable transmission according to claim 1, characterized in that the drive of the worm wheel is effected by a rotatably mounted on a hollow shaft and axially displaceable wing coupling.
  8. Continuously variable transmission according to claim 1, characterized in that the occurring during loading, resulting from the circumferential forces supporting moment is transmitted to the friction bodies through the guided in a gap in the ring carrier Reibkörperträger.
  9. Continuously variable transmission according to claim 1, characterized in that the ring carrier and the planet carrier rotatably and axially displaceably mounted on a hollow shaft, wherein the hollow shaft leads to the outside, there to be able to intercept the supporting moment.
  10. Stepless transmission according to claim 1, characterized in that the driving ring has at its periphery slots in which radially engage the spreader coupling cylinder pins.
DE102011016672A 2011-04-09 2011-04-09 Stepless gearbox for e.g. pedal electric cycle, has frictional bodies whose rotational axis is inclined to main axis and lies tangential or perpendicular to imaginary cylindrical periphery of main axis Withdrawn DE102011016672A1 (en)

Priority Applications (1)

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DE102011016672A DE102011016672A1 (en) 2011-04-09 2011-04-09 Stepless gearbox for e.g. pedal electric cycle, has frictional bodies whose rotational axis is inclined to main axis and lies tangential or perpendicular to imaginary cylindrical periphery of main axis

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DE102011016672A DE102011016672A1 (en) 2011-04-09 2011-04-09 Stepless gearbox for e.g. pedal electric cycle, has frictional bodies whose rotational axis is inclined to main axis and lies tangential or perpendicular to imaginary cylindrical periphery of main axis

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Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105324299A (en) * 2013-04-19 2016-02-10 福博科知识产权有限责任公司 Continuously variable transmission
US9878717B2 (en) 2008-08-05 2018-01-30 Fallbrook Intellectual Property Company Llc Systems and methods for control of transmission and/or prime mover
US9878719B2 (en) 2007-02-01 2018-01-30 Fallbrook Intellectual Property Company Llc Systems and methods for control of transmission and/or prime mover
US9903450B2 (en) 2008-08-26 2018-02-27 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US9920823B2 (en) 2009-04-16 2018-03-20 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US9945456B2 (en) 2007-06-11 2018-04-17 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US9950608B2 (en) 2005-10-28 2018-04-24 Fallbrook Intellectual Property Company Llc Electromotive drives
US10036453B2 (en) 2004-10-05 2018-07-31 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10047861B2 (en) 2016-01-15 2018-08-14 Fallbrook Intellectual Property Company Llc Systems and methods for controlling rollback in continuously variable transmissions
US10056811B2 (en) 2007-04-24 2018-08-21 Fallbrook Intellectual Property Company Llc Electric traction drives
US10066712B2 (en) 2010-03-03 2018-09-04 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US10066713B2 (en) 2008-06-23 2018-09-04 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10094453B2 (en) 2007-02-16 2018-10-09 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US10100927B2 (en) 2007-11-16 2018-10-16 Fallbrook Intellectual Property Company Llc Controller for variable transmission
US10197147B2 (en) 2010-11-10 2019-02-05 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10253880B2 (en) 2008-10-14 2019-04-09 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10260607B2 (en) 2007-02-12 2019-04-16 Fallbrook Intellectual Property Company Llc Continuously variable transmissions and methods therefor
US10260629B2 (en) 2007-07-05 2019-04-16 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10400872B2 (en) 2015-03-31 2019-09-03 Fallbrook Intellectual Property Company Llc Balanced split sun assemblies with integrated differential mechanisms, and variators and drive trains including balanced split sun assemblies
US10428915B2 (en) 2012-01-23 2019-10-01 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US10428939B2 (en) 2003-02-28 2019-10-01 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10458526B2 (en) 2016-03-18 2019-10-29 Fallbrook Intellectual Property Company Llc Continuously variable transmissions, systems and methods

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5834259A (en) * 1981-08-21 1983-02-28 Toshihiro Kondo Friction type stepless speed change gear
DE4127030A1 (en) 1991-08-16 1993-02-18 Fichtel & Sachs Ag A drive with infinitely variable transmission ratio
US20030125152A1 (en) * 2002-01-03 2003-07-03 Ikitake Yosikane Ratio differential type continuously variable speed transmission
WO2009111328A1 (en) 2008-02-29 2009-09-11 Fallbrook Technologies Inc. Continuously and/or infinitely variable transmissions and methods therefor
US20100120577A1 (en) * 2008-11-07 2010-05-13 Industrial Technology Research Institute Speed adjusting mechanism for roller traction toroidal continuously variable transmission

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5834259A (en) * 1981-08-21 1983-02-28 Toshihiro Kondo Friction type stepless speed change gear
DE4127030A1 (en) 1991-08-16 1993-02-18 Fichtel & Sachs Ag A drive with infinitely variable transmission ratio
US20030125152A1 (en) * 2002-01-03 2003-07-03 Ikitake Yosikane Ratio differential type continuously variable speed transmission
WO2009111328A1 (en) 2008-02-29 2009-09-11 Fallbrook Technologies Inc. Continuously and/or infinitely variable transmissions and methods therefor
US20100120577A1 (en) * 2008-11-07 2010-05-13 Industrial Technology Research Institute Speed adjusting mechanism for roller traction toroidal continuously variable transmission

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10428939B2 (en) 2003-02-28 2019-10-01 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10036453B2 (en) 2004-10-05 2018-07-31 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US9950608B2 (en) 2005-10-28 2018-04-24 Fallbrook Intellectual Property Company Llc Electromotive drives
US9878719B2 (en) 2007-02-01 2018-01-30 Fallbrook Intellectual Property Company Llc Systems and methods for control of transmission and/or prime mover
US10260607B2 (en) 2007-02-12 2019-04-16 Fallbrook Intellectual Property Company Llc Continuously variable transmissions and methods therefor
US10094453B2 (en) 2007-02-16 2018-10-09 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US10056811B2 (en) 2007-04-24 2018-08-21 Fallbrook Intellectual Property Company Llc Electric traction drives
US9945456B2 (en) 2007-06-11 2018-04-17 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10260629B2 (en) 2007-07-05 2019-04-16 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10100927B2 (en) 2007-11-16 2018-10-16 Fallbrook Intellectual Property Company Llc Controller for variable transmission
US10066713B2 (en) 2008-06-23 2018-09-04 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US9878717B2 (en) 2008-08-05 2018-01-30 Fallbrook Intellectual Property Company Llc Systems and methods for control of transmission and/or prime mover
US9903450B2 (en) 2008-08-26 2018-02-27 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10253880B2 (en) 2008-10-14 2019-04-09 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US9920823B2 (en) 2009-04-16 2018-03-20 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10066712B2 (en) 2010-03-03 2018-09-04 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US10197147B2 (en) 2010-11-10 2019-02-05 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10428915B2 (en) 2012-01-23 2019-10-01 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
CN105324299A (en) * 2013-04-19 2016-02-10 福博科知识产权有限责任公司 Continuously variable transmission
US9677650B2 (en) * 2013-04-19 2017-06-13 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10323732B2 (en) 2013-04-19 2019-06-18 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US20160040763A1 (en) * 2013-04-19 2016-02-11 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10400872B2 (en) 2015-03-31 2019-09-03 Fallbrook Intellectual Property Company Llc Balanced split sun assemblies with integrated differential mechanisms, and variators and drive trains including balanced split sun assemblies
US10047861B2 (en) 2016-01-15 2018-08-14 Fallbrook Intellectual Property Company Llc Systems and methods for controlling rollback in continuously variable transmissions
US10458526B2 (en) 2016-03-18 2019-10-29 Fallbrook Intellectual Property Company Llc Continuously variable transmissions, systems and methods

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