NL2035167A - Actuatable bidirectional clutch mechanism for a bicycle transmission - Google Patents

Actuatable bidirectional clutch mechanism for a bicycle transmission Download PDF

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Publication number
NL2035167A
NL2035167A NL2035167A NL2035167A NL2035167A NL 2035167 A NL2035167 A NL 2035167A NL 2035167 A NL2035167 A NL 2035167A NL 2035167 A NL2035167 A NL 2035167A NL 2035167 A NL2035167 A NL 2035167A
Authority
NL
Netherlands
Prior art keywords
coupling part
coupling
rotation
cam
complementary
Prior art date
Application number
NL2035167A
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 NL2035167A priority Critical patent/NL2035167A/en
Publication of NL2035167A publication Critical patent/NL2035167A/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: Actuatable bidirectional clutch mechanism for a bicycle transmission Abstract The disclosure relates to an actuatable bidirectional clutch mechanism for a bicycle transmission. The actuatable bidirectional clutch mechanism is arranged for being selectively actuated to a first state for preventing rotation of a selective one of the plurality of sun gears in a first rotational direction, and to a second state for preventing rotation of the selective one sun gear in a second, reverse, rotational direction.

Description

P35137NL00
Title: Actuatable bidirectional clutch mechanism for a bicycle transmission
FIELD
The mvention relates to an actuatable bidirectional clutch mechanism for a transmission for a bicycle.
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 is an object to propose an improved actuatable clutch for a bicycle transmission. In a more general sense it 1s 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 an actuatable bidirectional clutch mechanism for a bicycle transmission. The actuatable bidirectional clutch mechanism comprises a first clutch member connected or connectable to a clutch input or a clutch output, and having a first engagement surface; and a second clutch member connected or connectable to a clutch output or a clutch input, and having a complementary first engagement surface. The first clutch member is rotatable relative to the second clutch member. The actuatable bidirectional clutch mechanism is arranged for selectively being in a first state or a second state. The first engagement surface and the complementary first engagement surface are arranged for engaging each other in the first state of the actuatable bidirectional clutch mechanism for preventing rotation of the first clutch member relative to the second clutch member in a first rotational direction. 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 are arranged for engaging each other in the second state of the actuatable bidirectional clutch mechanism for preventing rotation of the first clutch member relative to the second clutch member in a second, reverse, rotational direction.
Hence, the actuatable bidirectional clutch mechanism can be used to selectively clutch two rotational members in two opposing rotational directions.
Optionally, the actuatable bidirectional clutch mechanism in the first state allows for rotation of the first clutch member relative to the second clutch member in the second rotational direction. Hence, the actuatable bidirectional clutch mechanism can for example be arranged to brake a rotational member in one direction while allowing the rotational member to be freewheel in the opposing rotational direction.
Optionally, the actuatable bidirectional clutch mechanism in the second state allows for rotation of the first clutch member relative to the second clutch member in the first rotational direction.
Optionally, the actuatable bidirectional clutch mechanism is configured for being engaged and disengaged under load.
Optionally, the actuatable bidirectional clutch mechanism is arranged for selectively being in a third state for allowing rotation of the first clutch member relative to the second clutch member in the first and in the second rotational direction.
Optionally, the actuatable bidirectional clutch mechanism cannot simultaneously be in more than one state.
Optionally, the actuatable bidirectional clutch mechanism cannot simultaneously be in the first state as well as in the second state.
Optionally, the actuatable bidirectional clutch mechanism cannot simultaneously be in the first state as well as in the third state. Optionally, the actuatable bidirectional clutch mechanism cannot simultaneously be in the second state as well as in the third state.
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 state 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, in the first state, permit freewheeling of the first clutch member relative to the second clutch member in the second rotational direction. Hence, in the first state, 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 for example be part of a teethed ratchet structure.
Optionally, the first pawl is pivotably arranged relative to a remainder of the first clutch member for, in the first state, 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 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 state to prevent rotation of the first clutch member relative to the second clutch member in the second rotational direction, and wherein the second pawl is pivotable about a fourth pivot axis to, in the second state, permit freewheeling of the first clutch member relative to the second clutch member in the first rotational direction. Hence, in the second state, 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 state, 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 in 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. 5 Optionally, the actuatable bidirectional clutch mechanism comprises an actuation member including a cam, the cam being arranged for being adjusted relative to the second clutch member between a first cam position associated with the first state or a second cam position associated with the second state, 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 relative to the second clutch member to a third cam position associated with the third state, wherein the cam in the third cam position releases the complementary first abutment surface and the complementary second abutment surface for disengagement from respectively the first abutment surface and the second abutment surface, for decoupling the second clutch member from the first clutch member.
Optionally, the actuation member is movable to a first actuation position in which a first cam and a second cam are in mutually different cam positions. 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.
Another aspect provides a clutch unit comprising a plurality of actuatable bidirectional clutch mechanisms as described herein.
Optionally, each actuatable bidirectional clutch mechanism is arranged for clutching a respective sun gear of a planetary gear set to a stationary axle. Each actuatable bidirectional clutch mechanism may also be arranged for clutching a respective ring gear of a planetary gear set to a stationary axle.
Optionally, the second clutch members of the plurality of actuatable bidirectional clutch mechanisms are non-rotatably coupled to each other. The second clutch members may be mounted to, or form, the stationary axle.
Optionally, the actuation members of the plurality of actuatable bidirectional clutch mechanisms are coupled to, or integrated with, each other to form a single integrated actuation member, e.g. a cam shaft, comprising a plurality of cams, wherein each cam is arranged for cooperating with a respective second clutch member.
An aspect provides a bicycle transmission comprising a planetary gear set including a ring gear, a planet carrier carrying one or more planet gears, and a sun gear, and an actuatable bidirectional clutch mechanism as described herein. The actuatable bidirectional clutch mechanism may be arranged for selectively clutching the sun gear to a stationary axle in a selective one of two rotational directions. The transmission may be embodied as a hub transmission or as a crank transmission.
An aspect provides a bicycle transmission comprising a transmission input and a transmission output, and a planetary gear set arranged between the transmission input and the transmission output. The planetary gear set having 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 bicycle transmission comprises a clutch unit as described herein. The clutch unit may be arranged for selectively clutching at least one of the plurality of sun gears to the stationary axle in a selective one of two rotational directions. The transmission may be embodied as a hub transmission or as a crank transmission.
A further aspect provides a bicycle comprising a bicycle 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 actuatable bidirectional clutch mechanism apply equally to the clutch unit, 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 1A-C and 2A-2C show examples of an actuatable bidirectional clutch mechanism;
Figures 3A-3B show an example of a bicycle transmission;
Figure 4 shows an example of a bicycle.
DETAILED DESCRIPTION
Figures 1A-1C and 2A-2C show two examples of an actuatable bidirectional clutch mechanism C2. The actuatable bidirectional clutch mechanism C2 comprises a first clutch member 2. The first clutch member 2 may be connected or connectable to an input, e.g. a rotational member of a planetary gear set such as a sun gear. The actuatable bidirectional clutch mechanism C2 also comprises a second clutch member 4. The second clutch member may be connected or connectable to an output, e.g. a stationery axle. 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 is in the first state, 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 state of the actuatable bidirectional clutch mechanism C2 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 1A-1C, formed by a ratchet structure 2a. The first engagement surface 6.1 and the second engagement surface 6.2 are in the example of figures 2A-2C, 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 actuatable bidirectional clutch mechanism C2 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 state or a second cam position associated with the second state. The cam 19 in the first cam position, as shown in figures 1A and 2A, locks the complementary first abutment surface 8.1 in engagement with the first abutment surface 6.1. The cam 19 particularly lifts the pawl 4a and retains the pawl 4a in the lifted position for allowing the complementary first abutment surface 8.1 to be engaged by the first abutment surface 6.1. The cam 19 in the second cam position, as shown in figures 1B and 2B, locks the complementary second abutment surface 8.2 in engagement with the second abutment surface 6.2. The cam 19 particularly lifts the pawl 4b and retains the pawl 4b in the lifted position for allowing the complementary second abutment surface 8.2 to be engaged by the second abutment surface 6.2. Hence, figure 1A and 2A show the actuatable bidirectional clutch mechanism C2 in the first state, and figure 1B and 2B show the actuatable bidirectional clutch mechanism C2 in the second state.
Figures 1C and 2C show the actuatable bidirectional clutch mechanism C2 in the third state. The cam 19 is in this example arranged for being adjusted to a third cam position associated with the optional third state. 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. The cam 19 particularly releases the pawls 4a and 4b for it to return to its initial position. Hence, the cam 19 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 is selectively adjustable between the first, second and third states. 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. 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. Instead of controlling the actuatable bidirectional clutch mechanisms C2 by rotation of the actuation member, the actuatable bidirectional clutch mechanisms C2 may additionally or alternatively be controlled by axial translation of an actuation member 10.
Figures 3A-3B show an example of a bicycle transmission 1000, comprising an actuatable bidirectional clutch mechanism C2, here two actuatable bidirectional clutch mechanism C2.1 C2.2. In this example, the transmission 1000 is 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 he 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 127a 127b, here two. The ring gear 128 meshes with one of the different planet radii 127a, 127b. The planetary gear set 100 also comprises a plurality of different sun gears 129a, 129b, here two. The two sun gears 129a, 129b respectively mesh with the two different planet radii 127a, 127b.
The sun gears 129a, 129b 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 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 121s hence parallel to the second actuatable clutch mechanism C1.2.
In a first state, both the first and the second actuatable clutch mechanisms C1.1, C1.2 are unclutched, such that torque can be transmitted 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 a second state, both the first and the second actuatable clutch mechanisms C1.1, C1.2 are clutched, such that torque can be transmitted 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 and second actuatable clutch mechanism C1.1, C1.2 enable 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.
The transmission 1000 can hence operates as an underdrive, reducing the rotational speed from the input I to the output O, and as an overdrive, increasing the rotational speed from the input I to the output O.
In an optional third state, the first actuatable clutch mechanism
C1.1 is clutched, while the second actuatable clutch mechanism C1.2 is unclutched, or vice versa. In the optional 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, comprising, here, two actuatable bidirectional clutch mechanisms C2.1, C1.2. Each actuatable bidirectional clutch mechanism
C2.1, C.2 is associated with respective sun gear 1294, 129b, for clutching the associated sun gear 129a, 129b to the stationary axle 30 in a selective one of two opposing rotation directions. Each actuatable bidirectional clutch mechanism C2.1, C2.2 is arranged for being selectively in a first state or a second state. In their first states, the actuatable bidirectional clutch mechanisms C2.1, C2.2 prevent rotation of the respective sun gear 1294, 129b in the first rotation direction about the stationary axle 30. In their second states, the actuatable bidirectional clutch mechanisms C2.1, C2.2 prevent rotation of the respective sun gear 1294, 129b in the second rotation direction about the stationary axle 30.
The direction in which a sun gears 1294, 129b are to be braked 1s1n this example dependent on the state of the first and second actuatable clutches C1.1, C1.2. For example, if the first and second actuatable clutches
C1.1, C1.2 are unclutched, a selective one of the actuatable bidirectional clutch mechanisms C2.1, C2.i may prevent rotation of a respective sun gear 129a, 129b in the second rotational direction, whereas if the first and second actuatable clutches C1.1, C1.2 are clutched, a selective one of the actuatable bidirectional clutch mechanisms C2.1, C2.2 may prevent rotation of a respective sun gear 129a, 129b 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 actuatable clutch C1.1 and the second actuatable clutch C1.2 are unclutched, 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 129a, 129b in the second, reverse, rotational direction. By braking a selective one of the sun gears
129a, 129b in the second rotational direction with the actuatable bidirectional clutch mechanisms C2.1, C2.2, 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 actuatable clutch
C1.1 and the second actuatable clutch C1.2 are clutched 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 129a, 129b in the first rotational direction. By braking a selective one of the sun gears 129a, 129b in the first rotational direction with the actuatable bidirectional clutch mechanisms C2.1, C2.2, 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 C2.2 may be arranged to prevent rotation of the sun gear 129a, 129b in one direction, while permitting rotation of the sun gear in the opposite rotation direction, e.g. by freewheeling. Hence, in the first state, the actuatable bidirectional clutch mechanism C2.1, C2.2 may be configured for permitting freewheeling of the sun gear 129a, 129b in the second rotational direction. Also, in the second state, the actuatable bidirectional clutch mechanism C2.1, C2.2 may be configured for permitting freewheeling of the sun gear 129a, 129b in the first rotational direction.
One or more of the actuatable bidirectional clutch mechanisms
C2.1, C2.2 may also selectively be adjusted to a third state. In the third state, the actuatable bidirectional clutch mechanism C2.1, C2.2 may allow free rotation of the respective sun gear 129a, 129b in both rotational directions about the stationary axle 30. One or more of the actuatable bidirectional clutch mechanisms C2.1, C2.2 may be adjusted to be in their third states, 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, C2.2 may also be adjusted to be in their first states, for allowing the ring gear 128 and the planet carrier 126 to corotate about the stationary axle 30 in the first rotational direction.
The transmission 1000 as exemplified in figure 3 can be a four- speed or a five-speed transmission 1000. Exemplary clutch states of the different actuatable clutches C1.1, C1.2, C2.1, C2.2 for the five-speed transmission 1000 are summarized in table 1.
In the example of table 1, the transmission 1000 is a five-speed transmission that includes a unitary transmission ratio. this gear may however be omitted to obtain a four-speed transmission. 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 the example of table 1, the actuatable bidirectional clutch mechanisms C2.1 C2.2 also include the optional third state. Instead, the actuatable bidirectional clutch mechanisms C2.1 may be adjusted between the only the first state and the second state.
Table 2 shows an example of a four-speed transmission 1000, in which the actuatable bidirectional clutches C2.1, C2.2 do not include a third state, but are switched only between their respective first and second states.
The exemplary transmission 1000 of table 2 also does not include a unitary gear. 1 (0.76) | unclutched ross
Figure 4 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 (25)

ConclusiesConclusions 1. Actueerbare bidirectioneel koppelingsmechanisme voor een fietstransmissie, omvattende: een met een koppelingsingang of een koppelingsuitgang verbonden of verbindbaar eerste koppelingsdeel met een eerste aangrijpingsoppervlak; en een met een koppelingsuitgang of een koppelingsingang verbonden of verbindbaar tweede koppelingsdeel met een complementair eerste aangrijpingsoppervlak; waarbij het actueerbare bidirectionele koppelingsmechanisme is ingericht om selectief in een eerste toestand of een tweede toestand te zijn; waarbij het eerste aangrijpingsoppervlak en het complementaire eerste aangrijpingsoppervlak zijn ingericht om elkaar aan te grijpen in de eerste toestand van het actueerbare bidirectionele koppelingsmechanisme om rotatie van het eerste koppelingsdeel ten opzichte van het tweede koppelingsdeel in een eerste rotatierichting te voorkomen; waarbij het eerste koppelingsdeel verder een tweede aangrijpingsoppervlak omvat, en het tweede koppelingsdeel verder een complementair tweede aangrijpingsoppervlak omvat; waarbij het tweede aangrijpingsoppervlak en het complementaire tweede aangrijpingsoppervlak zijn ingericht om elkaar aan te grijpen in de tweede toestand van het actueerbare bidirectionele koppelingsmechanisme om rotatie van het eerste koppelingsdeel ten opzichte van het tweede koppelingsdeel in een tweede, tegengestelde, rotatierichting te voorkomen.1. Actuable bidirectional clutch mechanism for a bicycle transmission, comprising: a first coupling part connected or connectable to a clutch input or a clutch output and to a first engaging surface; and a second coupling part connected or connectable to a coupling output or a coupling input with a complementary first engaging surface; wherein the actuable bidirectional coupling mechanism is arranged to be selectively in a first state or a second state; wherein the first engagement surface and the complementary first engagement surface are arranged to engage each other in the first state of the actuable bidirectional coupling mechanism to prevent rotation of the first coupling part relative to the second coupling part in a first direction of rotation; wherein the first coupling part further comprises a second engaging surface, and the second coupling part further comprises a complementary second engaging surface; wherein the second engaging surface and the complementary second engaging surface are adapted to engage each other in the second state of the actuable bidirectional coupling mechanism to prevent rotation of the first coupling part relative to the second coupling part in a second, opposite, rotational direction. 2. Mechanisme volgens conclusie 1, waarbij het actueerbare bidirectionele koppelingsmechanisme in de eerste toestand rotatie van het eerste koppelingsdeel ten opzichte van het tweede koppelingsdeel in de tweede rotatierichting toelaat.2. Mechanism according to claim 1, wherein the actuable bidirectional coupling mechanism in the first condition allows rotation of the first coupling part relative to the second coupling part in the second direction of rotation. 3. Mechanisme volgens conclusie 1 of 2, waarbij het actueerbare bidirectionele koppelingsmechanisme in de tweede toestand rotatie van het eerste koppelingsdeel ten opzichte van het tweede koppelingsdeel in de eerste rotatierichting toelaat.3. Mechanism according to claim 1 or 2, wherein the actuable bidirectional coupling mechanism in the second condition allows rotation of the first coupling part relative to the second coupling part in the first direction of rotation. 4. Mechanisme volgens een der voorgaande conclusies, waarbij het actueerbare bidirectionele koppelingsmechanisme is ingericht om selectief in een derde toestand te zijn voor het toelaten van rotatie van het eerste koppelingsdeel ten opzichte van het tweede koppelingsdeel in de eerste en in de tweede rotatierichting.4. Mechanism according to any one of the preceding claims, wherein the actuable bidirectional coupling mechanism is designed to be selectively in a third state for allowing rotation of the first coupling part relative to the second coupling part in the first and in the second direction of rotation. 5. Mechanisme volgens een der voorgaande conclusies, waarbij het complementaire eerste aangrijpingsoppervlak door een complementaire eerste pal gevormd wordt.5. Mechanism according to any one of the preceding claims, wherein the complementary first engaging surface is formed by a complementary first pawl. 6. Mechanisme volgens conclusie 5, waarbij de complementaire eerste pal om een eerste scharnieras scharnierbaar is om het eerste aangrijpingsoppervlak en het complementaire eerste aangrijpingsoppervlak in de eerste toestand te laten aangrijpen om rotatie van het eerste koppelingsdeel ten opzichte van het tweede koppelingsdeel in de eerste rotatierichting te voorkomen, en waarbij de complementaire eerste pal om een tweede scharnieras scharnierbaar is om in de eerste toestand vrijloop van het eerste koppelingsdeel ten opzichte van het tweede koppelingsdeel in de tweede rotatierichting toe te laten.6. Mechanism according to claim 5, wherein the complementary first pawl is pivotable about a first hinge axis to engage the first engaging surface and the complementary first engaging surface in the first condition to allow rotation of the first coupling part relative to the second coupling part in the first direction of 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 in the first condition. 7. Mechanisme volgens een der voorgaande conclusies, waarbij het eerste aangrijpingsoppervlak door een eerste pal gevormd wordt.7. Mechanism according to any one of the preceding claims, wherein the first engaging surface is formed by a first pawl. 8. Mechanisme volgens conclusie 7, waarbij de eerste pal scharnierbaar ten opzichte van een rest van het eerste koppelingsdeel is voorzien om in de eerste toestand vrijloop van het eerste koppelingsdeel ten opzichte van het tweede koppelingsdeel in de tweede rotatierichting toe te laten.8. Mechanism according to claim 7, wherein the first pawl is pivotable relative to a remainder of the first coupling part to allow free movement of the first coupling part relative to the second coupling part in the second direction of rotation in the first condition. 9. Mechanisme volgens conclusie 8, waarbij het complementaire tweede aangrijpingsoppervlak door een complementaire tweede pal gevormd wordt.9. Mechanism according to claim 8, wherein the complementary second engaging surface is formed by a complementary second pawl. 10. Mechanisme volgens conclusie 9, waarbij de complementaire tweede pal om een derde scharnieras scharnierbaar is om het tweede aangrijpingsoppervlak en het complementaire tweede aangrijpingsoppervlak in de tweede toestand te laten aangrijpen om rotatie van het eerste koppelingsdeel ten opzichte van het tweede koppelingsdeel in de tweede rotatierichting te voorkomen, en waarbij de tweede pal om een vierde scharnieras scharnierbaar is om in de tweede toestand vrijloop van het eerste koppelingsdeel ten opzichte van het tweede koppelingsdeel in de eerste rotatierichting toe te laten.10. Mechanism according to claim 9, wherein the complementary second pawl is pivotable about a third hinge axis to engage the second engaging surface and the complementary second engaging surface in the second condition to allow rotation of the first coupling part relative to the second coupling part in the second direction of rotation. and wherein the 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 in the second condition. 11. Mechanisme volgens conclusie 9 of 10, waarbij het tweede aangrijpingsoppervlak door een tweede pal gevormd wordt.11. Mechanism according to claim 9 or 10, wherein the second engaging surface is formed by a second pawl. 12. Mechanisme volgens conclusie 11, waarbij de tweede pal scharnierbaar 1s voorzien om 1n de tweede toestand vrijloop van het eerste koppelingsdeel ten opzichte van het tweede koppelingsdeel in de eerste rotatierichting toe te laten.12. Mechanism according to claim 11, wherein the second pawl is pivotable to allow free movement of the first coupling part relative to the second coupling part in the first direction of rotation in the second condition. 13. Mechanisme volgens een der voorgaande conclusies, omvattende een actuatiedeel omvattende van een nok, waarbij de nok is ingericht om ten opzichte van het tweede koppelingsdeel versteld te worden tussen een met de eerste toestand geassocieerde eerste nokpositie of een met de tweede toestand geassocieerde tweede nokpositie, waarbij de nok in de eerste nokpositie het complementaire eerste aangrijpingsoppervlak in aangrijping met het eerste aangrijpmgsoppervlak vergrendelt om rotatie van het tweede koppelingsdeel ten opzichte van het eerste koppelingsdeel in de eerste rotatierichting te voorkomen, en de nok in de tweede nokpositie het complementaire tweede aanslagoppervlak in aangrijping met het tweede aanslagoppervlak vergrendelt om rotatie van het tweede koppelingsdeel ten opzichte van het eerste koppelingsdeel te voorkomen in de tweede rotatierichting.13. Mechanism according to any one of the preceding claims, comprising an actuation part comprising a cam, wherein the cam is designed to be adjusted relative to the second coupling part between a first cam position associated with the first state or a second cam position associated with the second state. , wherein the cam in the first cam position locks the complementary first engagement surface into engagement with the first engagement surface to prevent rotation of the second coupling part relative to the first coupling part in the first direction of rotation, and the cam in the second cam position locks the complementary second abutment surface into engagement with the second stop surface is locked to prevent rotation of the second coupling part relative to the first coupling part in the second direction of rotation. 14. Mechanisme volgens conclusie 13 wanneer afhankelijk van conclusie 4, waarbij de nok is ingericht om ten opzichte van het tweede koppelingsdeel versteld te worden naar een met de derde toestand geassocieerde derde nokpositie, waarbij de nok in de derde nokpositie het complementaire eerste aangrijpingsoppervlak en het complementaire tweede aangrijpingsoppervlak vrijgeeft voor ontkoppeling van respectievelijk het eerste aangrijpimgsoppervlak en het tweede aangrijpingsoppervlak, voor het ontkoppelen van het tweede koppelingsdeel van het eerste koppelingsdeel.14. Mechanism according to claim 13 when dependent on claim 4, wherein the cam is adapted to be adjusted relative to the second coupling part to a third cam position associated with the third condition, wherein the cam in the third cam position has the complementary first engaging surface and the releases a complementary second engaging surface for uncoupling the first engaging surface and the second engaging surface, respectively, for uncoupling the second coupling part from the first coupling part. 15. Mechanisme volgens conclusie 13 of 14, waarbij het actuatiedeel naar een eerste actuatiepositie beweegbaar is waarin een eerste nok en een tweede nok zich in onderling verschillende nokposities bevinden.15. Mechanism according to claim 13 or 14, 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. 16. Mechanisme volgens een der conclusies 13-15, waarbij het actuatiedeel naar een tweede actuatiepositie beweegbaar is waarin zowel de eerste nok als de tweede nok zich in dezelfde nokpositie zijn.16. Mechanism according to any of the claims 13-15, wherein the actuation part is movable to a second actuation position in which both the first cam and the second cam are in the same cam position. 17. Mechanisme volgens een der conclusies 13-16, omvattende een indexeermechanisme ingericht voor het verstellen van het actuatiedeel ten opzichte van het tweede koppelingsdeel tussen ten minste de eerste nokpositie en de tweede nokpositie.17. Mechanism according to any of the claims 13-16, comprising an indexing mechanism designed for adjusting the actuation part relative to the second coupling part between at least the first cam position and the second cam position. 18. Mechanisme volgens conclusie 17, waarbij het indexeersmechanisme geconfigureerd is voor het vertalen van een continue rotationele beweging, bijvoorbeeld van de uitgang van een elektrische actuator, naar een intermitterende rotationele beweging van het actueerdeel.The mechanism of claim 17, wherein the indexing mechanism is configured to translate a continuous rotational movement, for example from the output of an electric actuator, to an intermittent rotational movement of the actuating part. 19. Koppelingseenheid voor een fietstransmissie, omvattende een veelheid actueerbare bidirectionele koppelingsmechanismen volgens een der voorgaande conclusies.19. Clutch unit for a bicycle transmission, comprising a plurality of actuable bidirectional clutch mechanisms according to any one of the preceding claims. 20. Koppelingseenheid volgens conclusie 19, waarbij elk activeerbaar bidirectioneel koppelingsmechanisme is ingericht voor het koppelen van een respectief zonnewiel van een planetaire tandwielset aan een stationaire as.20. Coupling unit according to claim 19, wherein each activatable bidirectional coupling mechanism is adapted to couple a respective sun gear of a planetary gear set to a stationary shaft. 21. Koppelingseenheid volgens conclusie 19 of 20, waarbij de tweede koppelingsdelen van de veelheid actueerbare bidirectionele koppelingsmechanismen niet-roteerbaar met elkaar gekoppeld zijn.21. Coupling unit according to claim 19 or 20, wherein the second coupling parts of the plurality of actuable bidirectional coupling mechanisms are non-rotatably coupled to each other. 22. Koppelingseenheid volgens een der conclusies 19-21 wanneer afhankelijk van conclusie 13, waarbij de actueerdelen van de veelheid actueerbare bidirectionele koppelingsmechanismen aan elkaar gekoppeld of geintegreerd zijn om een enkel geintegreerd actuatiedeel te vormen, bijvoorbeeld een nokkenas, omvattende een veelheid nokken, waarbij elke nok is ingericht voor samenwerking met een respectievelijk tweede koppelingsdeel.22. Coupling unit according to any one of claims 19-21 when dependent on claim 13, wherein the actuating parts of the plurality of actuable bidirectional coupling mechanisms are coupled or integrated together to form a single integrated actuating part, for example a camshaft, comprising a plurality of cams, each cam is designed for cooperation with a respective second coupling part. 23. Fietstransmissie omvattende een planetaire tandwielset omvattende een ringwiel, een planeetdrager die een of meer planeetwielen draagt, en een zonnewiel, en een actueerbaar bidirectioneel koppelingsmechanisme volgens een der conclusies 1-18, waarbij het actueerbare bidirectionele koppelingsmechanisme is ingericht voor het selectief koppelen van het zonnewiel aan een stationaire as in een selectieve van twee rotatierichtingen.23. Bicycle transmission comprising a planetary gear set comprising a ring gear, a planet carrier carrying one or more planet gears, and a sun gear, and an actuable bidirectional clutch mechanism according to any one of claims 1-18, wherein the actuable bidirectional clutch mechanism is designed for selectively coupling the sun gear attached to a stationary shaft in a selective of two directions of rotation. 24. Fietstransmissie omvattende een transmissie-ingang en een transmissie-uitgang, een planetaire tandwielset voorzien tussen de transmissie-ingang en de transmissie-utgang, waarbij de planetaire tandwielset een planeetdrager omvat die een getrapt planeetwiel draagt met een veelheid planeetstralen, een veelheid zonnewielen die respectievelijk samenwerken met de veelheid planeetstralen, en een ringwiel dat samenwerkt met ten minste één van de veelheid planeetstralen, en een koppelingseenheid volgens een der conclusies 19-22, waarbij de koppelingseenheid is ingericht voor het selectief koppelen van ten minste één van de veelheid zonnewielen aan de stationaire as In een selectieve van twee rotatierichtingen.24. A bicycle transmission comprising a transmission input and a transmission output, a planetary gear set provided between the transmission input and the transmission output, the planetary gear set including a planet carrier carrying a stepped planet gear having a plurality of planet radii, a plurality of sun gears carrying respectively cooperating with the plurality of planetary rays, and a ring gear that cooperates with at least one of the plurality of planetary rays, and a coupling unit according to any one of claims 19-22, wherein the coupling unit is adapted for selectively coupling at least one of the plurality of sun gears to the stationary axis In a selective of two directions of rotation. 25. Fiets omvattende een fietstransmissie volgens conclusie 23 of 24.25. Bicycle comprising a bicycle transmission according to claim 23 or 24.
NL2035167A 2022-10-07 2023-06-23 Actuatable bidirectional clutch mechanism for a bicycle transmission NL2035167A (en)

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NL2033260A NL2033260B1 (en) 2022-10-07 2022-10-07 Bicycle transmission system
NL2034230 2023-02-27
NL2035167A NL2035167A (en) 2022-10-07 2023-06-23 Actuatable bidirectional clutch mechanism for a bicycle transmission

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2028096A1 (en) * 2007-08-23 2009-02-25 Urs Elsasser Multigear epicyclical gear hub
US20090230758A1 (en) * 2008-03-11 2009-09-17 Sram Deutschland Gmbh Bicycle Wheel Hub
US8777791B1 (en) * 2013-02-07 2014-07-15 Shimano Inc. Bicycle drive unit
US20190032729A1 (en) * 2017-07-31 2019-01-31 GM Global Technology Operations LLC Cycle lock system and method
DE102019204648A1 (en) * 2018-04-20 2019-10-24 Shimano, Inc. drive system

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2028096A1 (en) * 2007-08-23 2009-02-25 Urs Elsasser Multigear epicyclical gear hub
US20090230758A1 (en) * 2008-03-11 2009-09-17 Sram Deutschland Gmbh Bicycle Wheel Hub
US8777791B1 (en) * 2013-02-07 2014-07-15 Shimano Inc. Bicycle drive unit
US20190032729A1 (en) * 2017-07-31 2019-01-31 GM Global Technology Operations LLC Cycle lock system and method
DE102019204648A1 (en) * 2018-04-20 2019-10-24 Shimano, Inc. drive system

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