NL2035164A - Bicycle transmission - Google Patents

Bicycle transmission Download PDF

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Publication number
NL2035164A
NL2035164A NL2035164A NL2035164A NL2035164A NL 2035164 A NL2035164 A NL 2035164A NL 2035164 A NL2035164 A NL 2035164A NL 2035164 A NL2035164 A NL 2035164A NL 2035164 A NL2035164 A NL 2035164A
Authority
NL
Netherlands
Prior art keywords
transmission
clutch
rotation
disposition
complementary
Prior art date
Application number
NL2035164A
Other languages
Dutch (nl)
Inventor
Marie Van Druten Roëll
Original Assignee
Classified Cycling Bv
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
Priority claimed from NL2033260A external-priority patent/NL2033260B1/en
Application filed by Classified Cycling Bv filed Critical Classified Cycling Bv
Priority to NL2035164A priority Critical patent/NL2035164A/en
Publication of NL2035164A publication Critical patent/NL2035164A/en

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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
    • 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
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
    • 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
    • B62M11/16—Transmissions 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
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/24—Freewheels or freewheel clutches specially adapted for cycles
    • F16D41/26—Freewheels or freewheel clutches specially adapted for cycles with provision for altering the action
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/24—Freewheels or freewheel clutches specially adapted for cycles
    • F16D41/30—Freewheels or freewheel clutches specially adapted for cycles with hinged pawl co-operating with teeth, cogs, or the like
    • 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
    • F16H2003/445—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the input and the set of orbital gears
    • 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
    • F16H2003/447—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the set of orbital gears and the output
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0047—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising five forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0056—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2041—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with four engaging means
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2069—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using two freewheel mechanism
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2079—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches
    • F16H2200/2084—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches two freewheel mechanisms

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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)
  • Structure Of Transmissions (AREA)

Abstract

Title: Bicycle transmission Abstract The disclosure relates to a bicycle transmission comprising a planetary gear set arranged between an input and an output, wherein the planetary gear set has a planet carrier carrying a stepped planet gear with a plurality of planet radii, a plurality of sun gears respectively cooperating with the plurality of planet radii, and a ring gear cooperating with at least one of the plurality of planet radii. The transmission comprises a first clutch mechanism arranged for being adjustable between a first state for establishing a torque transmission from the input to the ring gear and from the planet carrier to the transmission output, and a second state for establishing a torque transmission from the input to the planet carrier and from the ring gear to the output. The transmission also comprises a second clutch mechanism arranged for selectively clutching one of the plurality of sun gears to a stationary axle.

Description

P35136NL00
Title: Bicycle transmission
FIELD
The invention relates to a transmission for a bicycle, particularly an internal hub or transmission.
BACKGROUND
Bicycle transmission systems traditionally include a derailleur for shifting a chain between a set of differently sized sprockets. More modern bicycle transmission systems include an internal transmission, wherein a gear mechanism is held by a housing. The housing can be arranged at the crank of the bicycle, or can be formed by a wheel hub shell of a bicycle driven wheel. Known gear mechanisms include a planetary transmission, and an actuatable clutch for changing a transmission ratio according to which the planetary transmission transmits rotary power.
SUMMARY
It 1s an object to propose an improved bicycle transmission, such as a bicycle hub transmission or a bicycle crank transmission. In a more general sense it is an object to overcome or ameliorate at least one of the disadvantages of the prior art, or at least provide alternative processes and structures that are more effective than the prior art. It is at the very least aimed to offering a useful choice and contribution to the existing art.
An aspect provides a bicycle transmission comprising a transmission input and a transmission output. The transmission comprises a planetary gear set arranged between the transmission input and the transmission output, wherein the planetary gear set has a planet carrier carrying a stepped planet gear with a plurality of planet radii, a plurality of sun gears respectively cooperating with the plurality of planet radii, and a ring gear cooperating with at least one of the plurality of planet radii. The transmission comprises a first clutch mechanism arranged for being adjustable between a first state for establishing a torque transmission from the input to the ring gear and from the planet carrier to the transmission output, and a second state for establishing a torque transmission from the input to the planet carrier and from the ring gear to the output. The transmission also comprises a second clutch mechanism arranged for selectively clutching at least one of the plurality of sun gears to a stationary axle. The transmission can hence provide a effective range of transmission ratios while being constructively compact for being housed by a hub or crank housing.
Optionally, the first clutch mechanism comprises a first actuatable clutch in a transmission path between the transmission input and the planet carrier, and a first freewheel in a transmission path between the input and the ring gear; and a second actuatable clutch in a transmission path between the ring gear and the output, and a second freewheel in a transmission path between the planet carrier and the output. Hence, torque can be transmitted through the planetary gear set in two opposing directions, e.g. from the ring gear to the planet carrier for obtaining a speed reduction, and from the planet carrier to the ring gear for obtaining a speed increase. This effectively increases the range of transmission ratios obtainable by the transmission, with minimal components.
Optionally, in the first state, the first actuatable clutch and the second actuatable clutch are both in an unclutched state, and wherein in the second state, the first actuatable clutch and the second actuatable clutch are both in a clutched state for transmitting torque in at least one rotation direction. In the first state, when both first and second actuatable clutches are unclutched, torque can be transmitted from the transmission input via the first freewheel to the ring gear, and from the planet carrier via the second freewheel to the transmission output. The torque transmission from the ring gear to the planet carrier provides a speed reduction. In the second state, when both the first and second actuatable clutches are clutched,
torque can be transmitted from the transmission input via the first actuatable clutch to the planet carrier, and from the ring gear via the second actuatable clutch to the transmission output; with the first freewheel and the second freewheel being overrun. The torque transmission from the planet carrier to the ring gear provides a speed reduction.
Optionally, the first actuatable clutch and the second actuatable clutch are form closed clutches, configured for transferring torque in at least one, such as two, rotational directions.
Optionally, the transmission comprises an electric actuator arranged for actuating the first actuatable clutch and the second actuatable clutch.
Optionally, the electric actuator is further arranged for actuating the at least one actuatable bidirectional clutch mechanism.
Optionally, the electric actuator comprises a first electric actuator arranged for actuating the first actuatable clutch, and a second electric actuator arranged for actuating the second actuatable clutch.
Optionally, the first actuatable clutch and the second actuatable clutch are independently actuatable.
Optionally, each one of the first actuatable clutch and the second actuatable clutch is configured for being coupled and decoupled under load.
Optionally, the second clutch mechanism comprises at least one actuatable bidirectional clutch mechanism arranged for being selectively actuated to a first disposition for preventing rotation of a selective one of the plurality of sun gears relative the stationary axle in a first rotational direction, and to a second disposition for preventing rotation of the selective one sun gear relative to the stationary axle in a second, reverse, rotational direction. Hence, the one sun gear can be selectively braked in a selective one of two opposing rotational directions, respectively associated with the first and second dispositions of the first clutch mechanism. For example, the one sun gear is braked in one rotational direction when the first clutch mechanism is in the first disposition, whereas the one sun gear is braked in the opposite rotational direction when the first clutch mechanism is in the second disposition.
Optionally, the at least one actuatable bidirectional clutch mechanism in the first disposition allows freewheeling of the selective one sun gear in the second rotational direction. Hence, the bidirectional clutch can be arranged to brake the one sun gear in the first rotational direction while allowing to be overrun in the second rotational direction. The at least one bidirectional clutch can hence be overrun, e.g. when another bidirectional clutch of the second clutch mechanism is engaged.
Optionally, the at least one actuatable bidirectional clutch mechanism is configured for being coupled and decoupled under load.
Optionally, the at least one actuatable bidirectional clutch mechanism in the second disposition allows freewheeling of the selective one sun gear in the first rotational direction. Hence, the bidirectional clutch can be arranged to brake the one sun gear in the second rotational direction while allowing to be overrun in the first rotational direction. The at least one bidirectional clutch can hence be overrun, e.g. when another bidirectional clutch of the second clutch mechanism is engaged.
Optionally, the at least one actuatable bidirectional clutch mechanism is arranged for selectively being in a third disposition for allowing rotation of the sun gear relative to the stationary axle in the first and in the second rotational direction. The third disposition allows the sun to freely rotate relative to the stationary axle in two opposing rotation directions.
Optionally, the actuatable bidirectional clutch mechanism cannot simultaneously be in more than one disposition.
Optionally, the actuatable bidirectional clutch mechanism cannot simultaneously be in the first disposition as well as in the second disposition. Optionally, the actuatable bidirectional clutch mechanism cannot simultaneously be in the first disposition as well as in the third disposition. Optionally, the actuatable bidirectional clutch mechanism cannot simultaneously be in the second disposition as well as in the third disposition. 5 Optionally, the at least one actuatable bidirectional clutch mechanism comprises a first clutch member connected or connectable to the respective sun gear or the stationary axle, and having a first engagement surface; and a second clutch member connected or connectable to the stationery axle or the respective sun gear, and having a complementary first engagement surface, the first engagement surface and the complementary first engagement surface being arranged for selectively engaging each other in the first disposition for preventing rotation of the first clutch member relative to the second clutch member in the first rotational direction. The first clutch member may be rotatable relative to the second clutch member.
The first and second clutch members may be concentrically arranged. The second clutch member may be within the first clutch member. Alternatively, the first clutch member may be within the second clutch member. The second clutch member may be non-rotationally mounted to the stationary axle.
Optionally, the complementary first engagement surface is formed by a complementary first pawl.
Optionally, the complementary first pawl is pivotable about a first pivot axis to have the first engagement surface and the complementary first engagement surface engage in the first disposition to prevent rotation of the first clutch member relative to the second clutch member in the first rotational direction, and wherein the complementary first pawl is pivotable about a second pivot axis to permit freewheeling of the first clutch member relative to the second clutch member in the second rotational direction.
Hence, in the first disposition, the at least one actuatable bidirectional clutch mechanism can freewheel, or be overrun, in the second rotational direction.
Optionally, the first engagement surface is formed by a first pawl.
The first pawl may be non-movably coupled to the first clutch member. The first pawl may for example be part of a teethed ratchet structure.
Optionally, the first pawl is pivotably arranged for, in the first disposition, permitting freewheeling of the first clutch member relative to the second clutch member in the second rotational direction. Hence, the first engagement surface and the complementary first engagement surface may both be formed by a respective pivotable pawl. The complementary first pawl may be actuatable, while the first pawl may be passive.
Optionally, the first clutch member further has a second engagement surface, and the second clutch member further has a complementary second engagement surface, the second engagement surface and the complementary second engagement surface being arranged for selectively engaging each other in the second disposition for preventing rotation of the first clutch member relative to the second clutch member in the second rotational direction.
Optionally, the complementary second engagement surface is formed by a complementary second pawl.
Optionally, the complementary second pawl is pivotable about a third pivot axis to have the second engagement surface and the complementary second engagement surface engage in the second disposition to prevent rotation of the first clutch member relative to the second clutch member in the second rotational direction, and wherein the complementary second pawl is pivotable about a fourth pivot axis to permit freewheeling of the first clutch member relative to the second clutch member in the first rotational direction. Hence, in the second disposition, the at least one actuatable bidirectional clutch mechanism can freewheel, or be overrun, in the first rotational direction.
Optionally, the second engagement surface is formed by a second pawl.
Optionally, the second pawl is pivotably arranged for, in the second disposition, permitting freewheeling of the first clutch member relative to the second clutch member in the first rotational direction. Hence, the second engagement surface and the complementary second engagement surface may both be formed by a respective pivotable pawl. The complementary second pawl may be actuatable, while the second pawl may be passive.
Optionally, in the first disposition, the second engagement surface and the complementary second engagement surface cannot engage each other. Hence, the actuatable bidirectional clutch mechanism in the first disposition may not simultaneously be also in the second disposition.
Optionally, in the second disposition, the first engagement surface and the complementary first engagement surface cannot engage each other.
Hence, the actuatable bidirectional clutch mechanism 1n the second disposition may not simultaneously be also in the first disposition.
Optionally, in the third disposition, the second engagement surface and the first engagement surface and the complementary first engagement surface cannot engage each other, and the complementary second engagement surface cannot engage each other. Hence, the actuatable bidirectional clutch mechanism in the third disposition may not simultaneously be also in the first and/or second disposition.
Optionally, the transmission comprises an actuation member including a cam, the cam being arranged for being adjusted between a first cam position associated with the first disposition or a second cam position associated with the second disposition, wherein the cam in the first cam position locks the complementary first abutment surface in engagement with the first abutment surface for preventing rotation of the second clutch member relative to the first clutch member in the first rotational direction, and the cam in the second cam position locks the complementary second abutment surface in engagement with the second abutment surface for preventing rotation of the second clutch member relative to the first clutch member in the second rotational direction.
Optionally, the cam is arranged for being adjusted to a third cam position associated with the third disposition, wherein the cam in the third cam position releases the complementary first abutment surface and the complementary second abutment surface for disengagement from the first abutment surface and the second abutment surface, for decoupling the second clutch member from the first clutch member.
Optionally, the planetary gear set comprises N sun gears, and wherein the second clutch mechanism comprises N actuatable bidirectional clutch mechanisms or N-1 actuatable bidirectional clutch mechanisms. Each actuatable bidirectional clutch mechanism may be substantially identical.
The actuatable bidirectional clutch mechanisms may be actuated by means of respective cam of the actuation member.
Optionally, the actuation member includes a plurality of cams, e.g.
N or N-1 cams, wherein each cam is arranged for cooperating with a respective actuatable bidirectional clutch mechanism. Each cam may hence be associated with a respective sun gear of the planetary gear set, for use in selectively braking a sun gear in a selective one of two rotational directions.
The cam shaft may be rotationally actuated about an axis parallel to the stationary axle.
Optionally, the actuation member may be movable to a first actuation position in which a first cam is and a second cam are in a different cam position. The first cam may for example be in its first cam position while the second cam may be in its second or third cam position. The first cam may alternatively be, for example, in its second cam position while the second cam may be in its first or third cam position.
Optionally, the actuation member may be movable to a second actuation position in which both the first cam and the second cam are in the same cam position, e.g. both in in their first, both in their second or both in their third cam positions.
Optionally, the mechanism comprises an indexing mechanism arranged for adjusting the actuation member relative to the second clutch member between at least the first cam position and the second cam position.
Optionally, the indexing mechanism is configured to translates a continuous rotational motion, e.g. of output of an electric actuator, into an intermittent rotational motion of the actuation member. The indexing mechanism may for example include a Geneva drive, or Maltese cross drive.
Optionally, the second clutch mechanism comprises a passive bidirectional clutch mechanism arranged for being passively adjustable between a first disposition for preventing rotation of a predetermined one of the plurality of sun gears relative to the stationary axle in a first rotational direction, and a second disposition for preventing rotation of the predetermined one sun gear relative to the stationary axle in a second, reverse, rotational direction. The passive bidirectional clutch mechanism may for example include a freewheel mechanism.
Optionally, the second clutch mechanism comprises a passive unidirectional clutch mechanism arranged for preventing rotation of a predetermined one of the plurality of sun gears relative to the stationary axle in a first rotational direction or a second rotational direction. The passive unidirectional clutch mechanism may for example include a freewheel mechanism.
Optionally, the passive bidirectional clutch mechanism in the first disposition allows freewheeling of the predetermined one sun gear in the second rotational direction.
Optionally, the passive bidirectional clutch mechanism in the second disposition allows freewheeling of the predetermined one sun gear in the first rotational direction.
Optionally, the transmission is selectively operable according to a plurality of different transmission ratios including a set of underdrive transmission ratios and a set of overdrive transmission ratios.
Optionally, the transmission is operable according to the set of underdrive transmission ratios when the first clutch mechanism is in its first state, and wherein the transmission is operable according to the set of overdrive transmission ratios when the first clutch mechanism is in its second state.
Optionally, the underdrive transmission ratios and the overdrive transmission ratios are respectively inverse to each other.
Optionally, the transmission comprises a predetermined upshift sequence and/or a predetermined downshift sequence through successive gears of the transmission, wherein the upshift sequence and/or the downshift sequence each includes a first sequence part of successive selective clutching of the plurality of sun gears to the stationary axle in a first predetermined order and a second sequence part of successive selective clutching of the plurality of sun gears to the stationary axle in a second predetermined order, wherein the first predetermined order is the reverse of the second predetermined order. Hence, for example, the first sequence part may include a selective clutching a first sun gear, a second sun gear and a third sun to the stationary axle in that order, whereas the second sequence part may include a selective clutching of the third sun gear, the second sun gear and the third sun gear to the stationary axle in that order. The upshift or downshift sequence may hence for example include a selective clutching of the sun gears in a predetermined order of: first, second, third, [...], third, second, first. The first sequence part may be associated with the set of underdrive transmission ratios and the second sequence part may be associated with the set of overdrive transmission ratios, or vice versa. The first sequence part may hence be associated with the first clutch mechanism being in the first state and the second sequence part may be associated with the first clutch mechanism being in the second state, or vice versa. The upshift sequence may be reverse to the downshift sequence.
More in general, according to an aspect is provided a transmission comprising a predetermined upshift sequence and/or a predetermined downshift sequence through successive gears of the transmission, such as via successive planet radii of a stepped planet gear, wherein the upshift sequence and/or the downshift sequence each includes a first sequence part of successive selective transmission of torque via the successive planet radii in a first predetermined order and a second sequence part of successive selective transmission of torque via the successive planet radii in a second predetermined order, wherein the first predetermined order is the reverse of the second predetermined order.
Optionally, the transmission is selectively operable according to a unitary transmission ratio.
Optionally, the first clutch mechanism is arranged for being adjustable to a third state for establishing a torque transmission from the input to the output according to a unitary transmission ratio.
Optionally, in the third state, one of the first actuatable clutch and the second actuatable clutch is in a clutched state, and another one of the first actuatable clutch and the second actuatable clutch is in the unclutched state. Hence, the transmission input and the transmission output may both be rotationally coupled to the same rotational member of the planetary gear set, e.g. both to the ring gear or both to the planet carrier.
Optionally, in the third state, each actuatable bidirectional clutch mechanism of the second clutch mechanism is either in its third disposition or its second disposition for allowing the sun gears to freely rotate relative to the stationary axle in the first rotational direction.
Optionally, the transmission comprises a hub shell for driven wheel, and wherein the planetary gear set is housed by the hub shell. The transmission may hence be a hub transmission for the bicycle, e.g. arranged in a transmission path between a rear sprocket and a driven wheel of the bicycle.
Optionally, the transmission comprises a crank housing for being arranged at a crank of the bicycle, and wherein the planetary gear set is housed by the crank housing. The transmission may hence be a crank transmission for the bicycle, e.g. arranged in a transmission path between a crank and a front chain ring of the bicycle.
Another aspect provides a bicycle transmission comprising a transmission input and a transmission output. The transmission comprises a planetary gear set arranged between the transmission input and the transmission output, wherein the planetary gear set has a planet carrier carrying a stepped planet gear with a plurality of planet radii, a plurality of ring gears respectively cooperating with the plurality of planet radii, and a sun gear cooperating with at least one of the plurality of planet radii. The transmission comprises a first clutch mechanism arranged for being adjustable between a first state for establishing a torque transmission from the input to the sun gear and from the planet carrier to the transmission output, and a second state for establishing a torque transmission from the input to the planet carrier and from the sung gear to the output. The transmission also comprises a second clutch mechanism arranged for selectively clutching one of the plurality of ring gears to a stationary part, e.g. a stationary housing such as stationary crank transmission housing.
The bicycle transmission may be embodied as a crank transmission.
Another aspect provides a bicycle, comprising a transmission as described herein.
It will be appreciated that any of the aspects, features and options described herein can be combined. It will particularly be appreciated that any of the aspects, features and options described in view of the transmission apply equally to the bicycle, and vice versa.
BRIEF DESCRIPTION OF THE DRAWINGS
Embodiments of the present invention will now be described in detail with reference to the accompanying drawings in which:
Figures 1-4 show examples of a transmission for a bicycle;
Figures 5 and 6 show examples of an actuatable bidirectional clutch mechanism;
Figure 7 shows an example of a bicycle.
DETAILED DESCRIPTION
Figures 1A,1B, 2A,2B, 3A,3B and 4A,4B show schematic examples of a transmission 1000 for a bicycle. In these examples, the transmission 1000 1s embodied as a hub transmission but it will be appreciated that the transmission may also be embodied as a crank transmission. The transmission 1000 includes a transmission input I and a transmission output O. Here, the transmission input I is connected to a rear sprocket 3 for engaging a chain or belt of an chain or belt drive 300. The sprocket 3 may be part of a cassette of sprockets, such as including two or three sprockets. In a particular example, the cassette of sprockets includes at most two or at most 3 sprockets. In the embodiment of a crank transmission, the transmission input I may be connected to a crank of the bicycle. Here, the transmission output O is connected to a hub shell 51, which may in turn be connected to a driven wheel of the bicycle. In the embodiment of a crank transmission, the transmission output O may be connected to a front chain ring of the chain or belt drive 300.
The transmission 1000 comprises a planetary gear set 100 arranged for providing a speed reduction and/or speed increase between the input I and the output O. The planetary gear set 100 comprises a ring gear 128 and a planet carrier 126 carrying one or more planet gears 127. The planet carrier 126 particularly carries one or more stepped planet gears 127 having multiple different planet radii 1271. The ring gear 128 meshes with one of the different planet radii 1271. The planetary gear set 100 also comprises a plurality of different sun gears 129i. The plurality of sun gears respectively mesh with the plurality of different planet radii 1271.
The sun gears 1291 are rotatably arranged about a stationary axle 30. The stationary axle 30 may be mounted to a frame of the bicycle, for supporting torque thereon.
The transmission 1000 comprises a first clutch mechanism C1, including a first actuatable clutch mechanism C1.1 and a second actuatable clutch mechanism C1.2. the first actuatable clutch mechanism C1.1 is arranged in a transmission path between the transmission input I and the planet carrier 126. The second actuatable clutch mechanism C1.2 is arranged in a transmission path between the ring gear 128 and the transmission output O. The transmission 1000 also comprises a first freewheel 11 in a transmission path between the transmission input I and the ring gear 128. The first freewheel 11 is hence parallel to the first actuatable clutch mechanism C1.1. The transmission 1000 also comprises a second freewheel 12 in a transmission path between the planet carrier 126 and the transmission output O. The second freewheel 12 is hence parallel to the second actuatable clutch mechanism C1.2.
The first clutch mechanism C1 is configured for selectively being in a first state or a second state. In the first state, both the first and the second actuatable clutch mechanisms C1.1, C1.2 are in an unclutched state. Torque can accordingly be transmitted in the first state from the transmission input
I via the first freewheel 11 to the ring gear 128 and from the planet carrier 127 via the second freewheel 12 to the transmission output O. The planetary gear set 100 provides a speed reduction from the ring gear 128 to the planet carrier 126 in accordance with the relative dimensions of the cooperating rotational members of the planetary gear set 100.
In the second state of the first clutch mechanism C1, both the first and the second actuatable clutch mechanisms C1.1, C1.2 are in a clutched state. Torque can accordingly be transmitted in the second state from the transmission input I via the first actuatable clutch mechanism C1.1 to the planet carrier 126 and from the ring gear 128 via the second actuatable clutch mechanism C1.2 to the transmission output O. The first freewheel 11 and the second freewheel 12 are overrun in the second state. The planetary gear set 100 provides a speed increase from the planet carrier 126 to the ring gear 128 in accordance with the relative dimensions of the cooperating rotational members of the planetary gear set 100.
Here, the transmission 1000 also comprises a third freewheel 13 arranged in series with the first actuatable clutch C1.1, and a fourth freewheel 14 arranged in series with the second actuatable clutch C1.2. The third and fourth freewheels 13 and 14 can prevent lockup of the transmission 1000 if the bicycle were to be rolled backwards.
The first clutch mechanism C1 enables for reversing a transmission path through the planetary gear set 100, e.g. from ring gear 128 to carrier 126 or vice versa, to effectively increase the range of transmission ratios of the transmission 1000 as whole. In the first state of the first clutch mechanism C1, the transmission 1000 operates according to an underdrive transmission ratio, reducing the rotational speed from the input I to the output O. In the second state of the first clutch mechanism C1, the transmission 1000 operates according to an overdrive transmission ratio, increasing the rotational speed from the input I to the output O.
The first clutch mechanism C1 may also be arranged for selectively being in a third state. In the third state, the first actuatable clutch mechanism C1.1 may be in its clutched state, while the second actuatable clutch mechanism C1.2 1s in its unclutched state, or vice versa. In the third state, the transmission input I and the transmission output O are coupled to the same rotational member of the planetary gear set 100, e.g. both to the planet carrier 126 or both to the ring gear 128. In the third state, the transmission may be operable according to a unitary transmission ratio, e.g. a transmission ratio of 1:1.
The transmission 1000 further comprises a second clutch mechanism C2. The second clutch mechanism C2 is arranged for selectively clutching a selective one of the plurality of sun gears 129i to the stationary axle 30. Hereto, the second clutch mechanism C2 comprises a plurality of actuatable bidirectional clutch mechanisms C2.1. Each actuatable bidirectional clutch mechanism C2.1 is associated with respective sun gear 1291, for clutching the associated sun gear 1291 to the stationary axle 30 in a selective one of two opposing rotation directions. Each actuatable bidirectional clutch mechanism C2.1 is arranged for being selectively in a first disposition or a second disposition. In the first disposition, the actuatable bidirectional clutch mechanism C2.1 prevents rotation of the respective sun gear 1291 in the first rotation direction about the stationary axle 30. In the second disposition, the actuatable bidirectional clutch mechanism C2.i prevents rotation of the respective sun gear 1291 in the second rotation direction about the stationary axle 30. The direction in which a sun gear 1291 is to be braked 1s dependent on the state of the first clutch mechanism C2. For example, if the first clutch mechanism is in its first state, a selective one of the actuatable bidirectional clutch mechanisms
C2.i may prevent rotation of a respective sun gear 1294 in the second rotational direction, whereas if the first clutch mechanism is in its second state, a selective one of the actuatable bidirectional clutch mechanisms C2.1 may prevent rotation of a respective sun gear 1294 in the first rotational direction.
When the transmission input I is driven in the first rotational direction about the stationary axle 30, while the first clutch mechanism C1 is in the first state, the ring gear 128 is also driven in the first rotational direction, and via the stepped planet gear 127, a rotational force is induced on the sun gears 129i in the second, reverse, rotational direction. By braking a selective one of the sun gears 1291 with the second clutch mechanism C2, torque can be transmitted from the ring gear 128 to the planet carrier 126, according to an underdrive transmission ratio. When the transmission input
I is driven in the first rotational about the stationary axle 30, while the first clutch mechanism C1 is in the second state however, the planet carrier 126 is also driven in the first rotational direction, and via the stepped planet gear 127, a rotational force is induced on the sun gears 1291 in the first rotational direction. By braking a selective one of the sun gears 1291 with the second clutch mechanism C2, torque can be transmitted from the planet carrier 126 to the ring gear 128 according to an overdrive transmission ratio.
The actuatable bidirectional clutch mechanisms C2.1 may be arranged to prevent rotation of the sun gear 129 in one direction, while allowing rotation of the sun gear in the opposite rotation direction, e.g. by freewheeling. Hence, in the first disposition, the actuatable bidirectional clutch mechanism C2.1 may be configured for allowing freewheeling of the sun gear 1291 in the second rotational direction. Also, in the second disposition, the actuatable bidirectional clutch mechanism C2.1 may be configured for allowing freewheeling of the sun gear 129i in the first rotational direction.
One or more of the actuatable bidirectional clutch mechanisms C2.1 of the second clutch mechanism may also selectively be adjusted to a third disposition. In the third disposition, the actuatable bidirectional clutch mechanism C2.i may allow free rotation of the respective sun gear 129 in both rotational directions about the stationary axle 30. One or more of the actuatable bidirectional clutch mechanisms C2.1 may be adjusted to be in the third disposition, if the first clutch mechanism is in its third state, for allowing the ring gear 128 and the planet carrier 126 to corotate about the stationary axle 30. This way, the transmission 1000 may provide a unitary transmission ratio between the input I and output O. If the first clutch mechanism is in its third state, one or more of the actuatable bidirectional clutch mechanisms C2.1 may also be adjusted to be in the first disposition, for allowing the ring gear 128 and the planet carrier 126 to corotate about the stationary axle 30 in the first rotational direction.
In figures 1A,1B and 2A,2B, the planetary gear set 100 comprises two sun gears 129a, 129b meshing with two respective planet radii 127a, 127b of the stepped planet gear 127. Also, the second clutch mechanism C2 comprises two actuatable bidirectional clutch mechanisms C2.1, C2.2, arranged for selectively clutching the respective sun gears 129a, 129b to the stationary axle 30. While Figure 1B shows a schematic example of the first and second actuatable clutches C1.1, C1.2 of the first clutch mechanism C1, figures 2B, 3B and 4B show an exemplary first clutch mechanism C1, such as described in WO2018199757A2.
The transmission 1000 as exemplified in figures 1 and 2 can be a four-speed or a five-speed transmission 1000. Exemplary clutch states of the first and second clutch mechanisms C1, C2 for the five-speed transmission 1000 are summarized in table 1.
Table 1
Gear C1.1 C1.2 C2.1 C2.2 ran
In figures 3A, 3B, the planetary gear set 100 comprises three sun gears 1294, 129b, 129c meshing with three respective planet radii 1274, 127b, 127c of the stepped planet gear 127. Also, the second clutch mechanism C2 comprises three actuatable bidirectional clutch mechanisms
C2.1, C2.2, C2.3, arranged for selectively clutching the respective sun gears 129a, 129b, 129c to the stationary axle 30. A six-speed or a seven-speed transmission 1000 can be hence be obtained. Exemplary clutch states of the first and second clutch mechanisms C1, C2 for the seven-speed transmission 1000 are summarized in table 2.
Table 2 ;
In figures 4A, 4B, the planetary gear set 100 comprises four sun gears 129a, 129b, 129c, 129d meshing with four respective planet radii 127a, 127b, 127c, 127d of the stepped planet gear 127. Also, the second clutch mechanism C2 comprises four actuatable bidirectional clutch mechanisms
C2.1, C2.2, C2.3, C2.4, arranged for selectively clutching the respective sun gears 129a, 129b, 129c, 129d to the stationary axle 30. An eight speed or nine-speed transmission 1000 can be hence be obtained. Exemplary clutch states of the first and second clutch mechanisms C1, C2 for the nine-speed transmission 1000 are summarized in table 3.
Table 3
Gear ci ci2 C21 C22 23 C24 (disposition) | (disposition) | (disposition) | (disposition) un-olutched &
- >
In tables 1-3, the transmission 1000 is operable according to a unitary transmission ratio, but this gear may optionally be omitted. The first clutch mechanism C1 may for example not include the third state, but may be adjusted only between the first state and the second state. Without the unitary gear, the first actuatable clutch C1.1 and the second actuatable clutch C1.2 can be actuated in synchrony with each other, switching both clutches C1.1, C1.2 simultaneously between their clutched and their unclutched state. This may simplify the actuation construction. A benefit of the unitary gear is an increase in transmission ratio range. Also, with the unitary gear, each upshift or downshift to a next higher or lower gear may involve only shifting one the first and second actuatable clutches C1.1, C1.2.
In tables 1-3, the actuatable bidirectional clutch mechanisms also include the optional third disposition. Instead, the actuatable bidirectional clutch mechanisms C2.1 may be adjusted between the only the first disposition and the second disposition.
Figures 5A-5C and 6A-6C show two examples of an actuatable bidirectional clutch mechanism C2.1 of the second clutch mechanism. The actuatable bidirectional clutch mechanism C2.i comprises a first clutch member 2 connected or connectable to the respective sun gear 1291, and a second clutch member 4 connected or connectable to the stationery axle 30.
The first clutch member 2 has a first engagement surface 6.1, and the second clutch member 4 has a complementary first engagement surface 8.1.
The first engagement surface 6.1 and the complementary first engagement surface 8.1 are arranged for selectively engaging each other, when the actuatable bidirectional clutch mechanism C2.1 is in the first disposition, for preventing rotation of the first clutch member 2 relative to the second clutch member 4 in the first rotational direction.
The first clutch member 2 further comprises a second engagement surface 6.2, and the second clutch member further comprises a complementary second engagement surface 8.2. The second engagement surface 6.2 and the complementary second engagement surface 8.2 are arranged for selectively engaging each other in the second disposition of the actuatable bidirectional clutch mechanism C2.i for preventing rotation of the first clutch member 2 relative to the second clutch member 4 in the second rotational direction. The complementary first engagement surface 8.1 and the complementary second engagement surface 8.2 may be formed by respective pawls 4a, 4b of the second clutch member 4. The pawls 4a, 4b may each be pivotably connected to a remainder 4c of the second clutch member 4. The first engagement surface 6.1 and the second engagement surface 6.2 are in the example of figures 5A-5C, formed by a ratchet body 2a.
The ratchet body 2a may be mounted to or integrated with the sun gear 1291. The first engagement surface 6.1 and the second engagement surface 6.2 are in the example of figures 6A-6C, formed by respective pawls 2b. The pawls 2b may be pivotable relative to a remainder of the first clutch member 2, for allowing freewheeling.
Here, the transmission 1000 comprises an actuation member 10.
The actuation member 10 is here embodied as, or comprises, a cam shaft.
The actuation member 10 includes a cam 19. The cam 19 is arranged for being adjusted between a first cam position associated with the first disposition or a second cam position associated with the second disposition.
The cam 19 in the first cam position, as shown in figures 5A and 6A, locks the complementary first abutment surface 8.1 in engagement with the first abutment surface 6.1. The cam 19 in the second cam position, as shown in figures 5B and 6B, locks the complementary second abutment surface 8.2 in engagement with the second abutment surface 6.2. Hence, figure 5A and 6A show the actuatable bidirectional clutch mechanism C2.1 in the first disposition, and figure 5B and 6B show the actuatable bidirectional clutch mechanism C2.11n the second disposition.
Figures 5C and 6C show the actuatable bidirectional clutch mechanism C2.1 in the third disposition. The cam 19 is in this example arranged for being adjusted to a third cam position associated with the optional third disposition. The cam 19 in the third cam position releases the complementary first abutment surface 8.1 and the complementary second abutment surface 8.2 for disengagement from the first abutment surface 6.1 and the second abutment surface 6.2 respectively. Hence, the cam in the third cam position allows free rotation of the first clutch unit 2 relative to the second clutch unit 4 in two rotational directions.
By rotation of the actuation member 10, the actuatable bidirectional clutch mechanism C2.1 is selectively adjustable between the first, second and third dispositions. The actuation member 10 may include a plurality of cams 19, e.g. distributed in axial direction along the actuation member, wherein each cam 19 is associated with a respective actuatable bidirectional clutch mechanism C2.1. The cams 19 may for instance be angularly staggered with respect to each other. Rotation of the actuation member 10 may hence control each of the plurality of actuatable bidirectional clutch mechanisms C2.1. The actuation member 10 may further also be used for controlling the first clutch mechanism C1, to adjust the first clutch mechanism between its respective states. Instead of controlling the actuatable bidirectional clutch mechanisms C2.1 and/or the actuatable clutches C1.1 by rotation of the actuation member, the actuatable bidirectional clutch mechanisms C2.1 and/or the actuatable clutches C1.1 may additionally or alternatively be controlled by translation of an actuation member.
Figure 7 shows a bicycle 10000. The bicycle 10000 comprises a frame 10002 with a front fork 10005 and a rear fork 10007, as well as a front wheel and a rear wheel 10011, 10013 located in the front and rear fork respectively. The bicycle 10000 further comprises a crank 10017, and a front chain wheel 10019. The bicycle 10000 comprises a transmission 1000, in this example embodied as a hub transmission. The bicycle 10000 also comprises an endless drive 300 including a sprocket 3 and the front chain wheel 10019, wherein a chain 10023 threads over the front chain wheel 10019 and the sprocket 3.
Herein, the invention is described with reference to specific examples of embodiments of the invention. It will, however, be evident that various modifications and changes may be made therein, without departing from the essence of the invention. For the purpose of clarity and a concise description features are described herein as part of the same or separate embodiments, however, alternative embodiments having combinations of all or some of the features described in these separate embodiments are also envisaged.
However, other modifications, variations, and alternatives are also possible. The specifications, drawings and examples are, accordingly, to be regarded in an illustrative sense rather than in a restrictive sense.
In the claims, any reference signs placed between parentheses shall not be construed as limiting the claim. The word ‘comprising’ does not exclude the presence of other features or steps than those listed in a claim.
Furthermore, the words ‘a’ and ‘an’ shall not be construed as limited to ‘only one’, but instead are used to mean ‘at least one’, and do not exclude a plurality. The mere fact that certain measures are recited in mutually different claims does not indicate that a combination of these measures cannot be used to an advantage.

Claims (39)

ConclusiesConclusions 1. Een fietstransmissie, omvattende een transmissie-ingang en een transmissie-uitgang een tussen de transmissie-ingang en de transmissie-uitgang voorziene planetaire tandwielset omvattende een planeetdrager die een getrapt planeetwiel draagt met een veelheid aan planeetstralen, een veelheid aan zonnewielen die respectievelijk met de veelheid aan planeetstralen samenwerken, en een ringwiel dat met ten minste een van de veelheid aan planeetstralen samenwerkt; een eerste koppelingsmechanisme dat verstelbaar is tussen een eerste toestand voor het tot stand brengen van een koppeltransmissie van de ingang naar het ringwiel en van de planeetdrager naar de transmissie- uitgang, en een tweede toestand voor het tot stand brengen van een koppeltransmissie van de ingang naar de planeetdrager en van het ringwiel naar de uitgang; en een tweede koppelingsmechanisme voor het selectief koppelen van ten minste een van de veelheid zonnewielen aan een stationaire as.1. A bicycle transmission, comprising a transmission input and a transmission output, a planetary gear set provided between the transmission input and the transmission output, comprising a planet carrier carrying a stepped planet gear with a plurality of planet radii, a plurality of sun gears respectively with the plurality of planetary rays interacting, and a ring gear interacting with at least one of the plurality of planetary rays; a first clutch mechanism adjustable between a first state for establishing torque transmission from the input to the ring gear and from the planet carrier to the transmission output, and a second state for establishing torque transmission from the input to the planet carrier and from the ring gear to the exit; and a second coupling mechanism for selectively coupling at least one of the plurality of sun gears to a stationary axle. 2. De transmissie volgens conclusie 1, waarbij het eerste koppelingsmechanisme een eerste actueerbare koppeling in een transmissiepad tussen de transmissie-ingang en de planeetdrager omvat, en een eerste vrijloop in een transmissiepad tussen de ingang en het ringwiel; en een tweede actueerbare koppeling in een transmissiepad tussen het ringwiel en de uitgang omvat, en een tweede vrijloop in een transmissiepad tussen de planeetdrager en de uitgang.The transmission of claim 1, wherein the first clutch mechanism includes a first actuable clutch in a transmission path between the transmission input and the planet carrier, and a first freewheel in a transmission path between the input and the ring gear; and a second actuable clutch in a transmission path between the ring gear and the output, and a second freewheel in a transmission path between the planet carrier and the output. 3. De transmissie volgens conclusie 2, waarbij in de eerste toestand de eerste actueerbare koppeling en de tweede actueerbare koppeling beide in een ontkoppelde toestand zijn, en waarbij in de tweede toestand de eerste actueerbare koppeling en de tweede actueerbare koppeling beide in een gekoppelde toestand voor het overbrengen van koppel in ten minste één rotatierichting zijn.3. The transmission of claim 2, wherein in the first state the first actuable clutch and the second actuable clutch are both in a disengaged state, and wherein in the second state the first actuable clutch and the second actuable clutch are both in a coupled state for transmitting torque in at least one direction of rotation. 4. De transmissie volgens conclusie 2 of 3, waarbij de eerste actueerbare koppeling en de tweede actueerbare koppeling vormgesloten koppelingen zijn, mgericht voor het overbrengen van koppel in ten minste één rotatierichting.4. The transmission according to claim 2 or 3, wherein the first actuable coupling and the second actuable coupling are form-fitting couplings, oriented to transmit torque in at least one direction of rotation. 5. De transmissie volgens een der conclusies 2-4, omvattende een elektrische actuator die 15 ingericht voor het actueren van de eerste actueerbare koppeling en de tweede actueerbare koppeling.5. The transmission according to any one of claims 2-4, comprising an electric actuator adapted to actuate the first actuable clutch and the second actuable clutch. 6. De transmissie volgens conclusie 5, waarbij de elektrische actuator verder is ingericht voor het actueren van het ten minste ene actueerbare bidirectionele koppelingsmechanisme.The transmission of claim 5, wherein the electric actuator is further arranged to actuate the at least one actuable bidirectional clutch mechanism. 7. De transmissie volgens een der conclusies 2-6, waarbij elk van de eerste actueerbare koppeling en de tweede actueerbare koppeling is ingericht om te worden gekoppeld en ontkoppeld onder last.7. The transmission according to any one of claims 2-6, wherein each of the first actuable coupling and the second actuable coupling is designed to be coupled and uncoupled under load. 8. De transmissie volgens een der voorgaande conclusies, waarbij het tweede koppelingsmechanisme ten minste één actueerbaar bidirectioneel koppelingsmechanisme omvat dat is ingericht om selectief te worden geactueerd naar een eerste dispositie voor het voorkomen van rotatie van een selectieve van het veelheid zonnewielen in een eerste rotatierichting, en naar een tweede dispositie voor het voorkomen van rotatie van het selectieve ene zonnewiel in een tweede, tegengestelde, rotatierichting.The transmission according to any one of the preceding claims, wherein the second clutch mechanism comprises at least one actuable bidirectional clutch mechanism adapted to be selectively actuated to a first disposition for preventing rotation of a selective one of the plurality of sun gears in a first direction of rotation, and to a second disposition for preventing rotation of the selective one sun gear in a second, opposite, rotational direction. 9. De transmissie volgens conclusie 8, waarbij het ten minste ene actueerbare bidirectionele koppelingsmechanisme in de eerste dispositie vrijloop van het selectieve ene zonnewiel in de tweede rotatierichting toelaat.The transmission of claim 8, wherein the at least one actuable bidirectional clutch mechanism in the first disposition allows free-wheeling of the selective one sun gear in the second direction of rotation. 10. De transmissie volgens conclusie 8 of 9, waarbij het ten minste ene actueerbare bidirectionele koppelingsmechanisme in de tweede dispositie vrijloop van het selectieve ene zonnewiel in de eerste rotatierichting toelaat.The transmission according to claim 8 or 9, wherein the at least one actuable bidirectional clutch mechanism in the second disposition allows free-running of the selective one sun gear in the first direction of rotation. 11. De transmissie volgens een der conclusies 8-10, waarbij het ten minste ene actueerbare bidirectionele koppelingsmechanisme is ingericht om selectief in een derde toestand te zijn voor het toelaten van rotatie van het zonnewiel ten opzichte van de stationaire as in de eerste en in de tweede rotatierichting.11. The transmission according to any one of claims 8-10, wherein the at least one actuable bidirectional clutch mechanism is arranged to be selectively in a third state for allowing rotation of the sun gear relative to the stationary axis in the first and in the second direction of rotation. 12. De transmissie volgens een der conclusies 8-11, waarbij het ten minste ene actueerbare bidirectionele koppelingsmechanisme een met het respectieve zonnewiel of de stationaire as verbindbare eerste koppelingsdeel omvat met eerste aangrijpingsoppervlak; en een met de stationaire as of het respectievelijke zonnewiel verbindbare tweede koppelingselement met een complementair eerste aangrijpingsoppervlak, waarbij het eerste aangrijpingsoppervlak en het complementaire eerste aangrijpingsoppervlak zijn ingericht om selectief met elkaar in aangrijping te zijn in de eerste dispositie voor het voorkomen van rotatie van het eerste koppelingsdeel ten opzichte van het tweede koppelingsdeel in de eerste rotatierichting.12. The transmission according to any one of claims 8-11, wherein the at least one actuable bidirectional coupling mechanism comprises a first coupling part that can be connected to the respective sun gear or the stationary shaft and has a first engaging surface; and a second coupling element connectable to the stationary shaft or the respective sun gear and having a complementary first engagement surface, wherein the first engagement surface and the complementary first engagement surface are arranged to selectively engage with each other in the first disposition to prevent rotation of the first coupling part relative to the second coupling part in the first direction of rotation. 13. De transmissie volgens conclusie 12, waarbij het complementaire eerste aangrijpingsoppervlak door een complementaire eerste pal gevormd wordt.The transmission of claim 12, wherein the complementary first engagement surface is formed by a complementary first pawl. 14. De transmissie volgens conclusie 13, waarbij de complementaire eerste pal om een eerste scharnieras scharnierbaar is om in de eerste dispositie het eerste aangrijpingsoppervlak en het complementaire eerste aangrijpingsoppervlak te laten aangrijpen om rotatie van het eerste koppelingselement ten opzichte van het tweede koppelingselement in de eerste rotatierichting te voorkomen, en waarbij de complementaire eerste pal om een tweede scharnieras scharnierbaar is om vrijloop van het eerste koppelingsdeel ten opzichte van de tweede koppelingsdeel in de tweede rotatierichting toe te laten.The transmission of claim 13, wherein the complementary first pawl is pivotable about a first pivot axis to engage the first engagement surface and the complementary first engagement surface in the first disposition to allow rotation of the first coupling element relative to the second coupling element in the first rotation, and wherein the complementary first pawl is pivotable about a second hinge axis to allow free movement of the first coupling part relative to the second coupling part in the second direction of rotation. 15. De transmissie volgens conclusie 13 of 14, waarbij het eerste aangrijpingsoppervlak door een eerste pal gevormd wordt.The transmission according to claim 13 or 14, wherein the first engaging surface is formed by a first pawl. 16. De transmissie volgens conclusie 15, waarbij de eerste pal scharnierbaar is voorzien om in de eerste dispositie vrijloop van het eerste koppelingsdeel ten opzichte van het tweede koppelingsdeel in de tweede rotatierichting toe te laten.The transmission according to claim 15, wherein the first pawl is pivotably provided to allow free running of the first coupling part in the first position relative to the second coupling part in the second direction of rotation. 17. De transmissie volgens een der conclusies 12-16, waarbij het eerste koppelingsdeel verder een tweede aangrijpingsoppervlak heeft, en het tweede koppelingsdeel verder een complementair tweede aangrijpingsoppervlak heeft, waarbij het tweede aangrijpingsoppervlak en het complementaire tweede aangrijpingsoppervlak ingericht zijn voor het selectief aangrijpen op elkaar in de tweede dispositie voor het voorkomen van rotatie van het eerste koppelingsdeel ten opzichte van het tweede koppelingsdeel in de tweede rotatierichting.17. The transmission according to any one of claims 12-16, wherein the first coupling part further has a second engagement surface, and the second coupling part further has a complementary second engagement surface, wherein the second engagement surface and the complementary second engagement surface are adapted to selectively engage each other in the second disposition for preventing rotation of the first coupling part relative to the second coupling part in the second direction of rotation. 18. De transmissie volgens conclusie 17, waarbij het complementaire tweede aangrijpingsoppervlak door een complementaire tweede pal gevormd wordt.The transmission according to claim 17, wherein the complementary second engagement surface is formed by a complementary second pawl. 19. De transmissie volgens conclusie 18, waarbij de complementaire tweede pal om een derde scharnieras scharnierbaar 1s om het tweede aangrijpingsoppervlak en het complementaire tweede aangrijpingsoppervlak in de tweede dispositie te laten aangrijpen om rotatie van het eerste koppelingsdeel ten opzichte van het tweede koppelingsdeel te voorkomen in de tweede rotatierichting, en waarbij de complementaire tweede pal om een vierde scharnieras scharnierbaar is om vrijloop van het eerste koppelingsdeel ten opzichte van het tweede koppelingsdeel in de eerste rotatierichting toe te laten.The transmission of claim 18, wherein the complementary second pawl is pivotable about a third pivot axis to engage the second engagement surface and the complementary second engagement surface in the second disposition to prevent rotation of the first coupling member relative to the second coupling member in the second direction of rotation, and wherein the complementary second pawl is pivotable about a fourth hinge axis to allow free movement of the first coupling part relative to the second coupling part in the first direction of rotation. 20. De transmissie volgens conclusie 18 of 19, waarbij het tweede aangrijpingsoppervlak door een tweede pal gevormd wordt.20. The transmission according to claim 18 or 19, wherein the second engaging surface is formed by a second pawl. 21. De transmissie volgens conclusie 20, waarbij de tweede pal scharnierbaar is voorzien om in de tweede dispositie vrijloop van het eerste koppelingsdeel ten opzichte van het tweede koppelingsdeel in de eerste rotatierichting toe te laten.21. The transmission according to claim 20, wherein the second pawl is pivotably provided to allow free running of the first coupling part relative to the second coupling part in the first direction of rotation in the second position. 22. De transmissie volgens een der conclusies 17-21, omvattende een actuatiedeel omvattende een nok, waarbij de nok is ingericht om te worden versteld tussen een met de eerste dispositie geassocieerde eerste nokpositie of een met de tweede dispositie geassocieerde tweede nokpositie, waarbij de nok in de eerste nokpositie het complementaire eerste aangrijpingsoppervlak in aangrijping met het eerste aangrijpingsoppervlak vergrendelt om rotatie van het tweede koppelingselement ten opzichte van het eerste koppelingselement in de eerste rotatierichting te voorkomen, en de nok in de tweede nokpositie de complementair tweede aangrijpingsoppervlak in aangrijping met het tweede aangrijpingsoppervlak vergrendelt om rotatie van het tweede koppelingsdeel ten opzichte van het eerste koppelingsdeel in de tweede rotatierichting te voorkomen.22. The transmission according to any one of claims 17-21, comprising an actuation part comprising a cam, wherein the cam is adapted to be adjusted between a first cam position associated with the first disposition or a second cam position associated with the second disposition, wherein the cam in the first cam position the complementary first engagement surface locks into engagement with the first engagement surface to prevent rotation of the second coupling element relative to the first coupling element in the first direction of rotation, and the cam in the second cam position locks the complementary second engagement surface into engagement with the second engagement surface locks to prevent rotation of the second coupling part relative to the first coupling part in the second direction of rotation. 23. De transmissie volgens conclusie 22 wanneer afhankelijk van conclusie 11, waarbij de nok is ingericht om te worden versteld naar een met de derde dispositie geassocieerde derde nokpositie, waarbij de nok in de derde nokpositie het complementaire eerste aangrijpingsoppervlak en het complementaire tweede aangrijpingsoppervlak vrijgeeft voor ontkoppeling van het eerste aangrijpingsoppervlak en het tweede aangrijpmgsoppervlak voor het ontkoppelen van het tweede koppelingsdeel van het eerste koppelingsdeel.The transmission of claim 22 when dependent on claim 11, wherein the cam is adapted to be adjusted to a third cam position associated with the third disposition, wherein the cam in the third cam position releases the complementary first engagement surface and the complementary second engagement surface for disconnecting the first engaging surface and the second engaging surface for disconnecting the second coupling part from the first coupling part. 24. De transmissie volgens conclusie 23, waarbij het actuatiedeel naar een eerste actuatiepositie beweegbaar 1s waarin een eerste nok en een tweede nok zich in onderling verschillende nokposities bevinden.24. The transmission according to claim 23, wherein the actuation part is movable to a first actuation position in which a first cam and a second cam are in mutually different cam positions. 25. De transmissie volgens conclusie 23 of 24, waarbij het actuatiedeel naar een tweede actuatiepositie beweegbaar is waarin de eerste nok en de tweede nok zich in dezelfde nokpositie bevinden.25. The transmission according to claim 23 or 24, wherein the actuation part is movable to a second actuation position in which the first cam and the second cam are in the same cam position. 26. De transmissie volgens een der conclusies 8-25, waarbij de planetaire tandwielset N zonnewielen omvat, en waarbij het tweede koppelingsmechanisme N of N-1 actueerbare bidirectionele koppelingsmechanismen omvat.The transmission according to any one of claims 8-25, wherein the planetary gear set comprises N sun gears, and wherein the second clutch mechanism comprises N or N-1 actuable bidirectional clutch mechanisms. 27. De transmissie volgens een der voorgaande conclusies, waarbij het tweede koppelingsmechanisme een passieve bidirectionele koppeling omvat ingericht om passief verstelbaar te zijn tussen een eerste dispositie voor het koppelen van een vooraf bepaalde van de veelheid zonnewielen aan de stationaire as in een eerste rotatierichting, en een tweede dispositie voor het koppelen van het vooraf bepaalde zonnewiel aan de stationaire as in een tweede, tegenstelde, rotatierichting.The transmission of any one of the preceding claims, wherein the second clutch mechanism includes a passive bidirectional clutch configured to be passively adjustable between a first disposition for coupling a predetermined one of the plurality of sun gears to the stationary shaft in a first rotational direction, and a second disposition for coupling the predetermined sun gear to the stationary shaft in a second, opposite, rotational direction. 28. De transmissie volgens conclusie 27, waarbij de passieve bidirectionele koppeling vrijloop van het vooraf bepaalde zonnewiel in de tweede rotatierichting toelaat in de eerste dispositie, en waarbij de passieve bidirectionele koppeling vrijloop van het vooraf bepaalde zonnewiel in de eerste rotatierichting toelaat in de tweede dispositie.The transmission of claim 27, wherein the passive bidirectional clutch allows freewheeling of the predetermined sun gear in the second direction of rotation in the first disposition, and wherein the passive bidirectional clutch allows freewheeling of the predetermined sun gear in the first direction of rotation in the second disposition . 29. De transmissie volgens een der voorgaande conclusies, waarbij de transmissie selectief bedienbaar is volgens een veelheid verschillende transmissieratio’s, omvattende een set onderdrive-transmissieratio’s en een set overdrive-transmissieratio’s.29. The transmission according to any one of the preceding claims, wherein the transmission is selectively operable according to a plurality of different transmission ratios, including a set of underdrive transmission ratios and a set of overdrive transmission ratios. 30. De transmissie volgens conclusie 29, waarbij de transmissie volgens de set onderdrive-transmissieratio’s bedienbaar is wanneer het eerste koppelingsmechanisme in zijn eerste toestand is, en waarbij de transmissie volgens de set van overdrive-transmissieratio’s bedienbaar is wanneer het eerste koppelingsmechanisme zich in zijn tweede toestand bevindt.The transmission of claim 29, wherein the transmission is operable according to the set of underdrive transmission ratios when the first clutch mechanism is in its first state, and wherein the transmission is operable according to the set of overdrive transmission ratios when the first clutch mechanism is in its second state. condition. 31. De transmissie volgens conclusie 29 of 30, waarbij de onderdrive- transmissieratio’s en de overdrive-transmissieratio’s respectievelijk elkaars inverse zijn.The transmission of claim 29 or 30, wherein the underdrive transmission ratios and the overdrive transmission ratios are the inverse of each other, respectively. 32. De transmissie volgens een der voorgaande conclusies, omvattende een vooraf bepaalde opschakelsequentie en/of een vooraf bepaalde afschakelsequentie door opeenvolgende versnellingen van de transmissie, waarbij de opschakelsequentie en/of de afschakelsequentie een eerste sequentiedeel van opeenvolgende selectieve koppelingen van de veelheid zonnewielen aan de stationaire as in een eerste vooraf bepaalde volgorde omvat en een tweede sequentiedeel van opeenvolgende selectieve koppeling van de veelheid zonnewielen aan de stationaire as in een tweede vooraf bepaalde volgorde omvat, waarbij de eerste vooraf bepaalde volgorde omgekeerd is aan de tweede vooraf bepaalde volgorde.32. The transmission according to any one of the preceding claims, comprising a predetermined upshift sequence and/or a predetermined downshift sequence through successive gears of the transmission, wherein the upshift sequence and/or the downshift sequence comprises a first sequence part of successive selective couplings of the plurality of sun gears to the said stationary shaft in a first predetermined order and comprising a second sequence portion of successive selective coupling of the plurality of sun gears to the stationary shaft in a second predetermined order, wherein the first predetermined order is the reverse of the second predetermined order. 33. De transmissie volgens een der voorgaande conclusies, waarbij de transmissie selectief volgens een unitaire transmissieratio bedienbaar is.33. The transmission according to any one of the preceding claims, wherein the transmission can be selectively operated according to a unitary transmission ratio. 34. De transmissie volgens een der voorgaande conclusies, waarbij het eerste koppelingsmechanisme is ingericht om verstelbaar te zijn naar een derde toestand voor het tot stand brengen van een koppeltransmissie van de ingang naar de uitgang volgens een unitaire transmissieratio.The transmission according to any one of the preceding claims, wherein the first coupling mechanism is arranged to be adjustable to a third state for establishing a coupling transmission from the input to the output according to a unitary transmission ratio. 35. De transmissie volgens conclusie 34, waarbij in de derde toestand één van de eerste actueerbare koppeling en de tweede actueerbare koppeling in een gekoppelde toestand is, en een andere van de eerste actueerbare koppeling en de tweede actueerbare koppeling in de ontkoppelde toestand is.The transmission of claim 34, wherein in the third state, one of the first actuable clutch and the second actuable clutch is in a coupled state, and another of the first actuable clutch and the second actuable clutch is in the disengaged state. 36. De transmissie volgens conclusie 34 of 35, waarbij in de derde toestand elk actueerbaar bidirectioneel koppelingsmechanisme van het tweede koppelingsmechanisme ofwel in zijn derde dispositie danwel zijn tweede dispositie is voor het vrij laten roteren de zonnewielen ten opzichte van de stationaire as in de eerste rotatierichting.The transmission of claim 34 or 35, wherein in the third state each actuable bidirectional clutch mechanism of the second clutch mechanism is either in its third position or its second disposition to freely rotate the sun gears relative to the stationary shaft in the first direction of rotation . 37. De transmissie volgens een der voorgaande conclusies, omvattende een naafschaal voor een aangedreven wiel, en waarbij de planetaire tandwielstel door de naafschaal behuisd is.37. The transmission according to any one of the preceding claims, comprising a hub shell for a driven wheel, and wherein the planetary gear set is housed by the hub shell. 38. De transmissie volgens een der conclusies 1-36, omvattende een crankhuis om te worden voorzien bij een crank van de fiets, en waarbij de planetaire tandwielstel door het crankhus behuisd is.The transmission according to any one of claims 1-36, comprising a crank housing to be provided with a crank of the bicycle, and wherein the planetary gear set is housed by the crank housing. 39. Fiets voorzien van een transmissie volgens een der voorgaande conclusies.39. Bicycle provided with a transmission according to any of the preceding claims.
NL2035164A 2022-10-07 2023-06-23 Bicycle transmission NL2035164A (en)

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4402344C1 (en) * 1994-01-27 1995-03-16 Fichtel & Sachs Ag Control device for ratchet-type locks for bicycle multi-speed drive hubs
EP2028096A1 (en) * 2007-08-23 2009-02-25 Urs Elsasser Multigear epicyclical gear hub
WO2018199757A2 (en) 2017-04-27 2018-11-01 Advancing Technologies B.V. Clutch system for a torque transmission
WO2021080431A1 (en) * 2019-10-25 2021-04-29 Advatech B.V. Transmission system

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4402344C1 (en) * 1994-01-27 1995-03-16 Fichtel & Sachs Ag Control device for ratchet-type locks for bicycle multi-speed drive hubs
EP2028096A1 (en) * 2007-08-23 2009-02-25 Urs Elsasser Multigear epicyclical gear hub
WO2018199757A2 (en) 2017-04-27 2018-11-01 Advancing Technologies B.V. Clutch system for a torque transmission
WO2021080431A1 (en) * 2019-10-25 2021-04-29 Advatech B.V. Transmission system

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