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GB2080452A - Variable speed gear box - Google Patents

Variable speed gear box Download PDF

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Publication number
GB2080452A
GB2080452A GB8122168A GB8122168A GB2080452A GB 2080452 A GB2080452 A GB 2080452A GB 8122168 A GB8122168 A GB 8122168A GB 8122168 A GB8122168 A GB 8122168A GB 2080452 A GB2080452 A GB 2080452A
Authority
GB
United Kingdom
Prior art keywords
gear
gear box
driving
wheel
carrier
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Withdrawn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
GB8122168A
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to GB8122168A priority Critical patent/GB2080452A/en
Publication of GB2080452A publication Critical patent/GB2080452A/en
Withdrawn legal-status Critical Current

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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/48—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members with members having orbital motion
    • F16H15/50—Gearings providing a continuous range of gear ratios
    • F16H15/52—Gearings 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M11/00—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels
    • B62M11/04—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio
    • B62M11/14—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears
    • B62M11/18—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears with a plurality of planetary gear units
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H37/086—CVT using two coaxial friction members cooperating with at least one intermediate friction member
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/088—Power-split transmissions with summing differentials, with the input of the CVT connected or connectable to the input shaft

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Transmission Devices (AREA)
  • Structure Of Transmissions (AREA)

Abstract

A variable speed gear box, particularly a hub gear box for a pedal cycle wheel, comprises a rotatable input member driving the planet carrier 14 of an epicyclic gear train having also an annular gear and a sun gear 10. The annular gear 9 is integral with or is attached to an output or driven member 1 rotatable relatively to the input or driving member 5. A variable ratio drive means 16 acts between the planet gear carrier 11 and the sun gear 10 of the epicyclic gear train and its ratio is adjusted between a value greater than unity and a value less than unity, thereby to vary the rotational speed of the output member. Where the gear box is a hub gear box of a pedal cycle, the input or driving member of the gear box is rotatable by the driven sprocket of the cycle, the output or driven member of the gear box is the housing of the gear box and the hub of the wheel and the variable ratio drive is changed by a cable 19 movable axially of the gear box and the wheel in one direction against the force of a return spring 23 by an angularly-oscillatable arm carrying an idler sprocket wheel engaging the driving run of the driving chain of a cycle, the arm being biased by spring means in a direction to maintain the driving run of the chain in tension. <IMAGE>

Description

SPECIFICATION Variable speed gear box The invention relates to a variable speed gear box and is particularly, but not exclusively, concerned with a variable speed hub gear box of a bicycle.
An object of the invention is to provide a variable speed hub gear box by which the rotational speed of the output member thereof is automatically adjusted in accordance with the torque applied by the driving chain and thereby to eliminate or reduce the variation of tractive effort required during each revolution of the pedal sprocket. However, the gear box may have other applications where adjustment of the rotational speed of the output member of the gear box with respect to that of the input member is required.
According to the invention, a variable speed gear box comprises a rotatable input or driving member; an epicyclic gear train having an annular gear, a sun gear, a plurality of planet gears and a planet gear carrier, of which the planet gear carrier is rotatable about a common axis of the annular and sun gears and is integral with or is attached to the input member and the annular gear is integral with or is attached to an output or driven member rotatable relatively to the input or driving member, a variable ratio drive means acting between the planet gear carrier and a gear of the epicyclic gear train other than a planet gear, and means for adjusting the ratio of the variable ratio drive means between a value greater than unity, through unity, and a value less than unity, thereby to vary the rotational speed of the output member.
Conveniently, the variable ratio drive means acts between the planet gear carrier and the sun gear.
The variable ratio drive means may comprise a plurality of barrel-like members arranged in a ring around the common axis of rotation of the epicyclic gear train and each rotatable about an axis inclined to the common axis and bodily slidable along said common axis, the peripheral surfaces of the barrel-like members being engaged by a pair of annular followers carried by the sun gear and the planet gear carrier respectively, whereby rotational drive is effected on rotation of the input or driving member between the planet gear carrier, the follower carrier thereby, the barrel-like members, the follower carried by the sun wheel and the sun wheel, the ratio of the drive depending upon the ratio of the effective distances from said common axis of the points of contact of the respective followers with the barrel-like members according to the instantaneous axial positions of the latter relative to the sun wheel.
The barrel-like members may each be in the form of a pair of frustums of a cone arranged coaxially of each other with their larger diameter end faces abutting, thereby to form a member which in axial cross-section is of hexagonal shape.
The barrel-like members are conveniently mounted on a carrier arranged co-axially of the common axis of the epicyclic gear train and which is movable along said common axis by an adjusting member.
In one particular application, the variable speed gear box as set out in the immediately preceding paragraph is a hub gear box of a bicycle, or other pedal cycle, said common axis being the axis of rotation of a driven wheel of the cycle, the input or driving member of the gear box being rotatable by the driven sprocket of the cycle, the output or driven member of the gear box being the housing of the gear box and the hub of the wheel, the common adjusting member being movable axially of the gear box and the wheel in one direction against the force of a return spring by a cable movable by an angulariy-oscillatable arm carrying an idler sprocket wheel engaging the driving run of the driving chain of a cycle, the arm being biased by spring means in a direction to maintain the driving run of the chain in tension.
By way of example, a variable speed hub gear box for the driven wheel of a bicycle or other pedal cycle is now described with reference to the accompanying drawings, in which: Figure 1 is an axial section through the gear box showing the gear box showing the variable ratio drive means in one extreme position; Figure 2 is a similar view of part of Figure 1 showing the variable ratio drive means in another extreme position; Figure 3 is a view on the line Ill-Ill in Figure 1; Figure 4 is a view on the line IV--IV in Figure 1; and Figure 5 is a diagram showing how an operating cable appearing in Figure 1 is moved by the driving chain of the bicycle.
Referring to Figures 1 and 3, the gear box comprises a generally cylindrical tubular housing 1 constituting the hub of the wheel and having annularflanges 2 on which the inner ends of the spokes of the wheel are located. The housing 1 has a closing end plate 3 screw-threaded thereto and mounted for free rotation on a central parttubular shaft 4. The other end of the housing contains an end collar 5 which is freely rotatable both with respect to the shaft 4 and to the housing 1. The collar 5 has a central spigot 6 on which the driven sprocket 7 (see Figure 5) of the wheel is carded, rotation of the sprocket 7 by the driving chain 31, shown in Figure 5, of the bicycle effecting rotation of the collar 5, which is the aforesaid input or driving member.The collar 5 is fixed to a planet gear carrier 14 co-axial with the housing 1 and carrying a plurality of (e.g., four) planet gears 11 of the epicyclic gear train. The latter also comprises an annular gear 9 carried by the housing 1 and engaging the planet gears 11.
The planet gears 11 are supported on shafts 13 extending from the planet gear carrier 14 which is rotatable within the housing 1 and relatively to the shaft 4 about the axis of the latter which is the common axis of the gear box. The epicyclic gear train also includes a sun gear 10 mounted on the sleeve 1 5 co-axially mounted on the shaft 4.
As described so far, the gear box comprises an epicycle gear train formed by the sun gear 1 0, the planet gears 11 and the annular gear 9 and the input or driving member 5 driven by the chain sprocket 7 drives the planet gear carrier 14, the annular gear 9 driving the hub 1 of the wheel.
The variable ratio drive means provided by the invention comprises a ring of, for example, four barrel-like members 16 which are mounted in a carrier coniprising a-ring 17 co-axially rotatably mounted on the sleeve 1 5 and a plate 18 rotatable on the shaft 4. Each barrel-like member 1 6 is in the form of a pair of frustums of a cone arranged co-axially of each other with their larger diameter end faces abutting, thereby to form a member which in axial cross-section is of hexagonal shape. The axis of rotation of each member 16 is inclined to the common axis of the shaft 4 and the gear box. The peripheral surface of each member 16 is engaged by an annular follower 20 which is part of the planet gear carrier 14 and an annular follower surface 21 on the sleeve 15.The ring 17, the plate 1 8 and the members 16 are slidable as a body in the axial direction of the gear box between one extreme position as shown in Figure 1 and another extreme position as shown In Figure 2. In the position shown in Figure 1 the radial distance between the axis of rotation of each member 1 6 and the follower 20 is less than the radial distance between the axis of rotation of the member 16 and the follower 21. Therefore there will be stepdown ratio between the planet gear carrier 14 which drives the members 16 and the sun gear 10 which is driven by the members 16. In the other extreme position of the members 16, as shown in Figure 2, the ratio will be reversed to a step-up drive. In between the two extreme positions of the members 16, there will be a 1:1 drive ratio, where the aforesaid radial distances are equal.The driving of the sun gear 10 by the planet gear carrier 14 through the members 16 will be in the opposite rotational direction and this will modify the rotation of the annular gear 9, and thus the output or driven member 1, being effected directly through the epicyclic gear train. The axial sliding of the members 16 is effected by a cable 19 extending through part of the shaft 4 and which pulls the plate 18 by a disc 22 fixed to the free end of the cable 1 9. This pushes the ring 1 7 against a return spring 23 which bears at its other end against the planet gear carrier 14.
The sprocket wheel 7 drives the collar 5 and hence the housing 1 by direct drive through the planet wheels 11. However due to the epicyclic gear train the resultant speed of the housing 1 will be determined by the input/output ratio of the epicyclic gear train. This ratio will be altered depending on the position of the members 1 6 as described hereinbefore depending upon the movement to the left as viewed in Figure 1, of the cable 19.
Referring now to Figure 5, the cable 1 9 is pulled by a bell-crank lever 27 pivoted at 28 between the axis of the sprocket 7 and the axis of the pedal sprocket 29. Each arm of the bell-crank lever 27 carries an idler sprocket 30 engaging the driving (upper) and return (lower) runs of the driving chain 31 respectively. The bell-crank lever 27 is biased by a spring 32 into the position in which the driving run of the chain is maintained in tension. Alternatively the bell crank lever 27 may be replaced by a single-arm lever carrying an idler sprocket engaging the driving (upper) run only of the chain 31 and biased by a spring to a position to maintain the driving run in tension, similarly to a de Railleur gear.With either arrangement when torque is applied to the pedal sprocket 29, the driving run of the chain 31 will tend to straighten and this will cause the cable 19 to be pulled to alter the axial position of the members 1 6 with respect to the sleeve 1 5 and therefore to alter the ratio of the epicyclic gear train. On reduction of torque on the pedal sprocket 29, the cable 1 9 will move in the reverse direction and so the members 1 6 will be moved in the opposite direction axially of the sleeve 15 by the return spring 23, thereby correspondingly altering the ratio of the epicyclic gear train. In this way variations of the torque, i.e.
excess torque, applied by the rider to the pedal sprocket 29 will tend to be reduced or the torque applied will tend to become uniform. Although the variable speed gear box described is particularly intended for use in a bicycle, it may have other applications.

Claims (7)

1. A variable speed gear box comprising a rotatable input or driving member; an epicyclic gear train having an annular gear, a sun gear, a plurality of planet gears and a planet gear carrier, of which the planet gear carrier is rotatable about a common axis of the annular and sun gears and is integral with or is attached to the input member and the annular gear is integral with or is attached to an output or driven member rotatable relatively to the input or driving member, a variable ratio drive means acting between the planet gear carrier and a gear of the epicyclic gear train other than a planet gear, and means for adjusting the ratio of the variable ratio drive means between a value greater than unity, through unity, and a value less than unity, thereby to vary the rotational speed of the output member.
2. A gear box as claimed in claim 1 in which the variable ratio drive means acts between the planet gear carrier and the sun gear.
3. A gear box as claimed in claim 2 in which the variable ratio drive means comprises a plurality of barrel-like members arranged in a ring around the common axis of rotation of the epicyclic gear train and each rotatable about an axis inclined to the common axis and bodily slidable along said common axis, the peripheral surfaces of the barrel-like members being engaged by a pair of annular followers carried by the sun gear and the planet gear carrier respectively, whereby rotational drive is effected on rotation of the input or driving member between the planet gear carrier, the follower carrier thereby, the barrel-like members, the follower carried by the sun wheel and the sun wheel, the ratio of the drive depending upon the ratio of the effective distances from said common axis of the points of contact of the respective followers with the barrel-like members according to the instantaneous axial positions of the latter relative to the sun wheel.
4. A gear box as claimed in claim 3 in which the barrel-like members are each in the form of a pair of frustums of a cone arranged co-axially of each other with their larger diameter end faces abutting, thereby to form a member which in axial cross-section is of hexagonal shape.
5. A gear box as claimed in claim 3 or 4 in which the barrel-like members are mounted on a carrier arranged co-axially of the common axis of the epicyclic gear train and which is movable along said common axis by an adjusting member.
6. A variable speed gear box as claimed in claim 5 which is a hub gear box of a pedal cycle, said common axis being the axis of rotation of a driven wheel of the cycle, the input or driving member of the gear box being rotatable by the driven sprocket of the cycle, the output or driven member of the gear box being the housing of the gear box and the hub of the wheel, the common adjusting member being movable axially of the gear box and the wheel in one direction against the force of a return spring by a cable movable by an angulariy-oscillatable arm carrying an idler sprocket wheel engaging the driving run of the driving chain of a cycle, the arm being biased by spring means in a direction to maintain the driving run of the chain in tension.
7. A variable speed gear box constructed and arranged substantially as described herein and shown in the accompanying drawings.
GB8122168A 1980-07-17 1981-07-17 Variable speed gear box Withdrawn GB2080452A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
GB8122168A GB2080452A (en) 1980-07-17 1981-07-17 Variable speed gear box

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB8023339 1980-07-17
GB8122168A GB2080452A (en) 1980-07-17 1981-07-17 Variable speed gear box

Publications (1)

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GB2080452A true GB2080452A (en) 1982-02-03

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GB8122168A Withdrawn GB2080452A (en) 1980-07-17 1981-07-17 Variable speed gear box

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Cited By (57)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0432742A1 (en) * 1989-12-12 1991-06-19 Fichtel &amp; Sachs AG Drive hub for a vehicle
EP0528381A1 (en) * 1991-08-16 1993-02-24 Fichtel &amp; Sachs AG Hub, particularly for bicycles, with continuously-variable transmission
EP0530597A3 (en) * 1991-09-03 1994-03-23 Artur Polnik
US6241636B1 (en) 1997-09-02 2001-06-05 Motion Technologies, Llc Continuously variable transmission
US6419608B1 (en) 1999-10-22 2002-07-16 Motion Technologies, Llc Continuously variable transmission
DE4439006C2 (en) * 1994-11-02 2002-10-24 Walter Stein Bicycle hub gear
US6551210B2 (en) 2000-10-24 2003-04-22 Motion Technologies, Llc. Continuously variable transmission
US6689012B2 (en) 2001-04-26 2004-02-10 Motion Technologies, Llc Continuously variable transmission
US7011600B2 (en) 2003-02-28 2006-03-14 Fallbrook Technologies Inc. Continuously variable transmission
US7166052B2 (en) 2003-08-11 2007-01-23 Fallbrook Technologies Inc. Continuously variable planetary gear set
US7214159B2 (en) 2003-08-11 2007-05-08 Fallbrook Technologies Inc. Continuously variable planetary gear set
US7455617B2 (en) 2004-07-21 2008-11-25 Fallbrook Technologies Inc. Rolling traction planetary drive
US7600771B2 (en) 2006-05-11 2009-10-13 Catadon Systems Llc Continuously variable drivetrain
US7600963B2 (en) 2005-08-22 2009-10-13 Viryd Technologies Inc. Fluid energy converter
US7632203B2 (en) 2005-10-28 2009-12-15 Fallbrook Technologies Inc. Electromotive drives
US7670243B2 (en) 2005-08-24 2010-03-02 Fallbrook Technologies, Inc. Continuously variable transmission
US7762919B2 (en) 2004-10-05 2010-07-27 Fallbrook Technologies Inc. Continuously variable transmission
USRE41892E1 (en) 1997-09-02 2010-10-26 Fallbrook Technologies Inc. Continuously variable transmission
US7871353B2 (en) 2005-12-09 2011-01-18 Fallbrook Technologies Inc. Continuously variable transmission
US7914029B2 (en) 2005-11-22 2011-03-29 Fallbrook Technologies Inc. Continuously variable transmission
US8087482B2 (en) 2006-03-14 2012-01-03 Fallbrook Technologies Inc. Wheelchair
US8167759B2 (en) 2008-10-14 2012-05-01 Fallbrook Technologies Inc. Continuously variable transmission
US8313405B2 (en) 2008-02-29 2012-11-20 Fallbrook Intellectual Property Company Llc Continuously and/or infinitely variable transmissions and methods therefor
US8313404B2 (en) 2007-02-16 2012-11-20 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US8317651B2 (en) 2008-05-07 2012-11-27 Fallbrook Intellectual Property Company Llc Assemblies and methods for clamping force generation
US8321097B2 (en) 2007-12-21 2012-11-27 Fallbrook Intellectual Property Company Llc Automatic transmissions and methods therefor
US8360917B2 (en) 2009-04-16 2013-01-29 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8376903B2 (en) 2006-11-08 2013-02-19 Fallbrook Intellectual Property Company Llc Clamping force generator
US8393989B2 (en) 2007-04-24 2013-03-12 Fallbrook Intellectual Property Company Llc Electric traction drives
US8398518B2 (en) 2008-06-23 2013-03-19 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8469856B2 (en) 2008-08-26 2013-06-25 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8480529B2 (en) 2006-06-26 2013-07-09 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8506452B2 (en) 2005-12-30 2013-08-13 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8512195B2 (en) 2010-03-03 2013-08-20 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US8535199B2 (en) 2008-06-06 2013-09-17 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
EP2669549A1 (en) * 2012-05-30 2013-12-04 Robert Bosch Gmbh Bicycle gears
US8641577B2 (en) 2007-06-11 2014-02-04 Fallbrook Intellectual Property Company Llc Continuously variable transmission
WO2014026754A1 (en) * 2012-08-11 2014-02-20 Peter Strauss Continuously variable transmission
US8738255B2 (en) 2007-02-01 2014-05-27 Fallbrook Intellectual Property Company Llc Systems and methods for control of transmission and/or prime mover
US8776633B2 (en) 2006-01-30 2014-07-15 Fallbrook Intellectual Property Company Llc System for manipulating a continuously variable transmission
US8818661B2 (en) 2008-08-05 2014-08-26 Fallbrook Intellectual Property Company Llc Methods for control of transmission and prime mover
WO2014147055A1 (en) * 2013-03-18 2014-09-25 Campus Rex GmbH & Co. KG Power-split transmission and method for optimizing the efficiency of and/or the range of gear ratios in a power-split transmission
US8845485B2 (en) 2011-04-04 2014-09-30 Fallbrook Intellectual Property Company Llc Auxiliary power unit having a continuously variable transmission
US8888643B2 (en) 2010-11-10 2014-11-18 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8900085B2 (en) 2007-07-05 2014-12-02 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8996263B2 (en) 2007-11-16 2015-03-31 Fallbrook Intellectual Property Company Llc Controller for variable transmission
US9328810B2 (en) * 2006-08-28 2016-05-03 Richard C. Raney Variable ratio gearmotor with interactive ratio control
WO2016083080A1 (en) * 2014-11-24 2016-06-02 Gerhard Kirschey Continuously variable bicycle gear system
US9371894B2 (en) 2007-02-12 2016-06-21 Fallbrook Intellectual Property Company Llc Continuously variable transmissions and methods therefor
US9611921B2 (en) 2012-01-23 2017-04-04 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US9677650B2 (en) 2013-04-19 2017-06-13 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
US10458526B2 (en) 2016-03-18 2019-10-29 Fallbrook Intellectual Property Company Llc Continuously variable transmissions, systems and methods
US11174922B2 (en) 2019-02-26 2021-11-16 Fallbrook Intellectual Property Company Llc Reversible variable drives and systems and methods for control in forward and reverse directions
US11215268B2 (en) 2018-11-06 2022-01-04 Fallbrook Intellectual Property Company Llc Continuously variable transmissions, synchronous shifting, twin countershafts and methods for control of same
US11667351B2 (en) 2016-05-11 2023-06-06 Fallbrook Intellectual Property Company Llc Systems and methods for automatic configuration and automatic calibration of continuously variable transmissions and bicycles having continuously variable transmission
CN116792473A (en) * 2023-06-30 2023-09-22 广州极飞科技股份有限公司 Speed change system, hub motor and agricultural unmanned vehicle

Cited By (245)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5069655A (en) * 1989-12-12 1991-12-03 Fichtel & Sachs Ag Driving hub for a vehicle
EP0432742A1 (en) * 1989-12-12 1991-06-19 Fichtel &amp; Sachs AG Drive hub for a vehicle
EP0528381A1 (en) * 1991-08-16 1993-02-24 Fichtel &amp; Sachs AG Hub, particularly for bicycles, with continuously-variable transmission
US5318486A (en) * 1991-08-16 1994-06-07 Fichtel & Sachs Ag Driving hub for a vehicle, particularly a bicycle, with an infinitely adjustable transmission ratio
EP0530597A3 (en) * 1991-09-03 1994-03-23 Artur Polnik
DE4439006C2 (en) * 1994-11-02 2002-10-24 Walter Stein Bicycle hub gear
US7393303B2 (en) 1997-09-02 2008-07-01 Fallbrook Technologies Inc. Continuously variable transmission
US7156770B2 (en) 1997-09-02 2007-01-02 Fallbrook Technologies Inc. Continuously variable transmission
US6322475B2 (en) 1997-09-02 2001-11-27 Donald C. Miller Continuously variable transmission
US7427253B2 (en) 1997-09-02 2008-09-23 Fallbrook Technologies Inc. Continuously variable transmission
US6676559B2 (en) 1997-09-02 2004-01-13 Motion Technologies, Llc Continuously variable transmission
US7320660B2 (en) 1997-09-02 2008-01-22 Fallbrook Technologies Inc. Continuously variable transmission
US6945903B2 (en) 1997-09-02 2005-09-20 Fallbrook Technologies, Inc. Continuously variable transmission
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