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
  • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
  • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
  • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
  • F16H3/089—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
• • 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
  • B62M11/06—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with spur gear wheels
• • 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
  • B62M25/00—Actuators for gearing speed-change mechanisms specially adapted for cycles
• • 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
  • F16D11/00—Clutches in which the members have interengaging parts
  • F16D11/08—Clutches in which the members have interengaging parts actuated by moving a non-rotating part axially
  • F16D11/10—Clutches in which the members have interengaging parts actuated by moving a non-rotating part axially with clutching members movable only axially
• • 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
  • F16D21/00—Systems comprising a plurality of actuated clutches
  • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
  • F16D21/04—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways with a shaft carrying a number of rotatable transmission members, e.g. gears, each of which can be connected to the shaft by a clutching member or members between the shaft and the hub of the transmission member
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D41/00—Freewheels or freewheel clutches
  • F16D41/24—Freewheels or freewheel clutches specially adapted for cycles
  • F16D41/36—Freewheels or freewheel clutches specially adapted for cycles with clutching ring or disc axially shifted as a result of lost motion between actuating members
• • 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
  • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
  • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
  • F16H3/10—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with one or more one-way clutches as an essential feature
• • 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
  • B62M17/00—Transmissions characterised by use of rotary shaft, e.g. cardan shaft
• • 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
  • B62M6/00—Rider propulsion of wheeled vehicles with additional source of power, e.g. combustion engine or electric motor
  • B62M6/40—Rider propelled cycles with auxiliary electric motor
  • B62M6/55—Rider propelled cycles with auxiliary electric motor power-driven at crank shafts parts
• • 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
  • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
  • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
  • F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
  • F16D2023/141—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings characterised by using a fork; Details of forks
• • 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
  • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
  • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
  • F16H2003/0818—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts comprising means for power-shifting
• • 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
  • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
  • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
  • F16H63/30—Constructional features of the final output mechanisms
  • F16H2063/3089—Spring assisted shift, e.g. springs for accumulating energy of shift movement and release it when clutch teeth are aligned

Definitions

• the invention relates to a gearbox.
• the aim of the invention is in particular to improve the feel, the performance and the reliability of gear ratio changes by avoiding breaks in torque, energy supply cuts when upshifting, the risk of false neutral, broken forks and/or gears in the gearbox.
• the invention finds particular application in the field of gearboxes for motor vehicles, with thermal or electric motors. Nevertheless, the invention can also be advantageously implemented in two-wheeled vehicles, motorized or not, or even in machine tools.
• a gearbox without torque break for a motor vehicle is generally a double-clutch gearbox. It conventionally comprises a primary shaft, connected to an electric or thermal motor, and two coaxial secondary shafts connected to the wheels of the vehicle. The primary shaft and the two secondary shafts are interconnected via gears forming the gear ratios. Each gear comprises a toothed wheel, fixedly linked in rotation to the primary shaft, and an idler gear mounted on one of the secondary shafts. The idler gears defining the even speed ratios are carried by one of the secondary shafts, and those defining the odd speed ratios are carried by the other secondary shaft. The idler gears rotate freely with respect to their secondary shaft except when a player joins one of the idler gears with their secondary shaft to engage the corresponding gear ratio. The players are each linked to a rigid fork, mobile in translation. The translation movement of the rigid forks is given by a control barrel.
• the gearbox further comprises a first clutch for controlling one of the secondary shafts and a second clutch to drive the other secondary shaft.
• a double-clutch gearbox requires a system for synchronizing said clutches to perform gear changes. When a higher gear must, for example, be engaged, the synchronization system automatically disengages the secondary shaft carrying the idler gear of the gear corresponding to the lower gear.
• Such a gearbox is complex.
• the gearbox has a primary shaft, which is also the crank axle, a single secondary shaft and a tertiary shaft, usually coaxial with the primary shaft.
• Radial pawls are mounted in the secondary shaft, on a coaxial axis. Each pawl secures respectively an idler gear with the secondary shaft to engage the corresponding gear ratio. Said pawls are driven by a mechanism internal to said secondary shaft.
• the PTO points in the idler gear/pawl connection are limited, whether in number (1 to 2 maximum), or in diameter due to being inside said shaft.
• the number of parts generally of small dimensions, their fragility and the complexity of their assembly have a significant impact on the reliability, cost and maintenance of the gearbox.
• the present invention aims to remedy the aforementioned drawbacks.
• the present invention proposes an alternative to existing gearboxes without a break in torque.
• the gearbox can advantageously be used for motor vehicles, with heat or electric motors, such as for example karts, cars, agricultural machinery, etc., just as for two-wheeled vehicles, motorized or not, such as cycles, motorcycles or electrically assisted bicycles, or for traditional or numerically controlled machine tools.
• motor vehicles with heat or electric motors, such as for example karts, cars, agricultural machinery, etc.
• motorized or not such as cycles, motorcycles or electrically assisted bicycles, or for traditional or numerically controlled machine tools.
• the gearbox according to the invention comprises at least two shafts, called primary shaft and secondary shaft, gears forming the ratios of speed, sliders for changing gear ratios, forks and a control barrel.
• Each gear comprises a toothed wheel, fixedly linked in rotation to one of the two shafts, and an idler pinion, mounted on the other shaft, which mesh with each other.
• Each idler gear has dogs.
• Each slider is configured to cooperate with one or two idler pinion(s).
• Each slider is able to move towards the associated idler pinion(s) or two by means of a fork.
• Each slider has dogs complementary to the dogs of the idler gear(s) with which it cooperates.
• Each fork has a guide pin. Said guide pin of a fork is secured thereto.
• the guide finger acts directly on the fork, it drives it directly.
• the guide finger and the fork can be made as a single piece.
• a fork has a blade.
• the blade preferably comprises a body and two branches connected to said body.
• the guide finger is integral with the blade of the fork, preferably integral with the body of the fork.
• a fork provided with a guide finger advantageously makes it possible to reduce the number of parts to be assembled in the gearbox, simplifying the mounting of the fork in said gearbox and thus making the gearbox more robust.
• the control barrel comprises guide members, each guide member being configured to guide the guide finger of a fork.
• All of the gearbox forks, sliding gears, idler gears and guide components form a gear selection system.
• a fork, a sliding gear, the associated idler pinion(s), and a guide member associated with the fork form the elements of a subassembly of said gear selection system.
• each sub-assembly comprises an elastic return means, this elastic return means being in particular configured to, when a new gear ratio is engaged, uncouple the idler pinion of the gear forming the previously engaged gear ratio.
• a single element of each sub-assembly comprises an elastic return means.
• Such an elastic return means advantageously makes it possible, during a gear change, to delay on the one hand the interconnection of a player with an idler gear when engaging a gear ratio and on the other apart from the clutch release of a walkman with an idler gear when disengaging from a previous gear ratio.
• dog clutch we mean the cooperation of a sliding gear with an idler gear, engaging a gear ratio formed by the gear comprising said idler gear.
• release is meant the extraction of the slider from an idler gear, disengaging the gear ratio formed by the gear including said idler gear.
• the invention also responds to the following characteristics, implemented separately or in each of their technically effective combinations.
• the movement of the guide finger drives the fork directly, that is to say the movement of the blade and therefore of the associated slider, independently of the elastic return means.
• the set of toothed wheels is fixedly linked to the primary shaft and the set of idler gears is mounted on the secondary shaft.
• the kinematic chain is as follows:
• the driving force acts on the primary shaft rotating the toothed wheels of the different speed ratios.
• the toothed wheels drive the various idler gears with which they are associated by meshing.
• each idler gear rotates the player with which it is clutched.
• each player being fixedly linked in rotation with the secondary shaft, drives the latter to ensure the driving output of the gearbox.
• the gearbox comprises a third shaft, called a tertiary shaft.
• the sprockets and idler gears are distributed on the three trees. Adding a tertiary shaft can be advantageous in the case of a cycle, where the primary shaft would be the crank axle and the tertiary shaft would be the gearbox output shaft.
• the tertiary shaft allows the direction of rotation to be identical to that of the primary shaft.
• the gearbox when a portable player cooperates with a single idler gear, the gearbox may comprise an odd number of gears, therefore an odd number of gear ratios.
• the player when a player cooperates with two idler gears, said player is interposed between two consecutive idler gears of the same shaft.
• the slider has two opposite side faces, and has at each of these side faces, claws intended to cooperate with the claws of the idler gear opposite.
• the fork in a subassembly, comprises the elastic return means.
• the fork comprises at least one flexible blade.
• Said at least one flexible blade forms the elastic return means.
• the at least one blade deforms elastically.
• one of the sliding gears is moved, by the associated fork, towards the idler pinion of the gear forming the desired gear ratio, to engage it.
• the blade of the fork When the claws of said player arrive at the level of the claws of the idler gear, if the claws cannot cooperate together because they are not in phase with each other, the blade of the fork, thanks to its elasticity, can bend temporarily and find itself under stress . As soon as the dogs of the player and those of the idler gear are in phase, the flexible blade of the fork, thanks to its elasticity, will automatically return to its state at rest, exerting a force of pressure on the player to push it towards the pinion crazy, coming to make them clutch and engage the desired gear.
• the flexible blade of the fork allows the walkman, which must be coupled with an idler gear, to wait for the phasing of the different dogs without effort.
• the slider which is clutched to the idler gear of the gear forming said gear ratio is moved, by the fork, to bring it back to a neutral position.
• the idler gear is under pressure and it is impossible to disengage the player from said idler gear.
• the flexible blade of the fork thanks to its elasticity, can bend temporarily and find itself under stress.
• the idler gear of the previous gear ratio will begin to rotate slower than the shaft carrying said idler gear and the pressure on the player will then be released.
• the dogs of said walkman and the dogs of the idler gear then uncouple naturally.
• the flexible blade of the fork thanks to its elasticity, will then automatically return to its state at rest, exerting a restoring force on the slider to bring it back to its neutral position after disengagement with the idler gear. Said idler gear again becomes free in rotation with respect to the shaft which carries it.
• the flexible blade of the fork thus allows the player, which must be uncoupled from the idler gear to return to its neutral position, to wait for the pressure on said idler gear to be released, gently, effortlessly and naturally.
• the fork guide finger in a sub-assembly, is a so-called oscillating guide finger, held in neutral by springs, the oscillating guide finger and the springs forming the means elastic return.
• the guide finger is partly housed in a core of the fork.
• the core comprises a through bore intended to receive a guide pin of the fork.
• the blade of the fork is a rigid blade.
• the core has a hole for the passage of said guide finger.
• one of the sliding gears is moved, by the associated fork, towards the idler gear of the gear forming the desired gear ratio, to dog it.
• the dogs of said player arrive at the level of the dogs of the idler gear, if the dogs cannot cooperate together because they are not in phase with each other, the movement of said player is blocked, simultaneously blocking the movement of the fork and of its core on the guide pin.
• the fork's guide finger continues to follow the movement of the track, shifting into the lumen of the core, and compressing one of the springs in said core, which then finds itself temporarily under stress.
• the compressed spring due to its elasticity, will automatically return to its state of rest, causing the displacement of the core of the fork along the guide axis, therefore the displacement of the blade of the fork and of the associated slider. Said player is thus pushed towards the idler gear, causing them to clutch together and engage the desired gear ratio.
• the elasticity of the springs allows the portable player, which must be coupled with an idler gear, to wait for the phasing of the various dogs without effort.
• the slider which is clutched to the idler gear of the gear forming said gear ratio is moved, by the fork, to bring it back to a neutral position.
• the idler gear is under pressure and it is impossible to disengage the player from said idler gear.
• the guide finger of the fork which continues to follow the track, shifts into the slot of the core, and compresses one of the springs in said core, which is then temporarily under stress.
• the idler gear of the previous gear will start to turn slower than the shaft carrying the said idler gear and the pressure on the player will then be released.
• the dogs of said walkman and the dogs of the idler gear then uncouple naturally.
• the compressed spring due to its elasticity, will automatically return to its state of rest, causing the movement of the core of the fork along the guide axis, therefore the movement of the blade of the fork and the associated slider. Said slider is thus moved laterally from the idler gear and returned to its neutral position after disengaging from the idler gear. Said idler gear becomes free in rotation with respect to the shaft which carries it.
• the elasticity of the spring thus allows the player, which must be uncoupled from the idler gear to return to its neutral position, to wait for the pressure on said idler gear to be released, gently, effortlessly and naturally.
• the or both idler pinion(s) comprise(s) the elastic return means.
• each idler gear comprises an external part, comprising a lateral bearing face, and a central part intended to be inserted into the outer part, said central part being provided with claws, said central part being connected in rotation to the outer part but free in translation.
• the elastic return means is in the form a spring positioned between the lateral bearing face of the outer part and the central part.
• the spring is held fixed at one end of the outer part and at another end at the central part.
• the blade of the fork is a rigid blade.
• one of the sliders is moved, by the associated fork, towards the idler pinion of the gear forming the desired gear ratio, to engage it.
• the elasticity of the spring allows the portable player, which must be coupled with an idler gear, to wait for the phasing of the various dogs without effort.
• the slider which is clutched to the idler gear of the gear forming said gear ratio is moved, by the fork, to bring it back to a neutral position.
• the idler gear is under pressure and it is impossible to disengage the player from said idler gear.
• the central part of the idler gear is driven with the slider, causing a slight stretching of the spring.
• the idler gear of the previous gear will start to turn slower than the shaft carrying said idler gear and the negative pressure (tension thanks to the anchoring of the ends of the spring) , on the player will then be released.
• the dogs of said walkman and the dogs of the idler gear then uncouple naturally.
• the spring will return to its state at rest, exerting a restoring force on the central part of said idler gear to move it away from the player and bring it back to the outer part of said idler gear.
• the idler gear becomes free to rotate relative to the shaft that carries it.
• the elasticity of the spring thus allows the player, which must be uncoupled from the idler gear to return to its neutral position, to wait for the negative pressure on said idler gear to be released, gently, effortlessly and naturally.
• the player in a sub-assembly, comparable to the idler gear, the player comprises the elastic return means.
• the slider comprises an external part, comprising a lateral support face, and a central part intended to be inserted into the external part, said central part being provided with claws, said central part being connected in rotation to the external part but free in translation.
• the elastic return means is in the form of a spring positioned between the lateral bearing face of the outer part and the central part.
• the spring is held fixed at one end of the outer part and at another end at the central part.
• the blade of the fork is a rigid blade.
• the guide member comprises the elastic return means.
• the guide member comprises:
• annular part attached to the control barrel, fixedly connected in rotation to said control barrel but movable in translation along a barrel axis and over a predefined distance, said annular part comprising a track extending on a circumferential surface thereof this,
• At least one spring arranged against said annular part, at the level of at least one side face of said annular part, said at least one spring being connected, by one end, to said annular part and, by another end, to a fixed stop on the control barrel, the at least one spring forming the elastic return means.
• the blade of the fork is preferably a rigid blade.
• the guide member comprises two springs, each spring being arranged on either side of the annular part, at opposite side faces of said annular part.
• Each spring is connected, by one end, to said annular part and, by another end, to a fixed stop on the control barrel. Said two springs form the elastic return means.
• the elasticity of at least one spring allows the portable player, which must be coupled with an idler gear, to wait for the phasing of the various dogs without effort.
• the slider which is clutched to the idler gear of the gear forming said gear ratio is moved, by the fork, to bring it back to a neutral position.
• the idler gear is under pressure and it is impossible to disengage the player from said idler gear.
• Movement of the slider is temporarily blocked, simultaneously blocking movement of the fork.
• the guide finger of the fork continuing to follow the track of the associated guide member, causes a shift of the annular part, stretching or compressing the at least one spring. The at least one spring is then temporarily under stress.
• the at least one spring due to its elasticity, will automatically return to its state of rest, causing the movement of the annular part on the control barrel, and consequently driving the fork, therefore the movement of the associated slider. Said walkman is thus moved away from the idler gear. Said idler gear again becomes free in rotation with respect to the shaft which carries it.
• the elasticity of at least one spring thus allows the player, which must be uncoupled from the idler gear to return to its neutral position, to wait for the negative pressure on said idler gear to be released, gently, effortlessly and naturally.
• the dogs of the sliding gears and of the idler gears of the gear selection system are dogs of the type with complementary wolf teeth.
• Wolf teeth are in the overall shape of saw teeth with two adjacent sides forming between them an angle less than or equal to 90°.
• the wolf teeth of a walkman are configured on the one hand to hook the wolf teeth of the idler gear with which it cooperates, causing the rotational drive of the shaft carrying said idler gear and on the other hand to escape in opposite direction, like freewheel pawls.
• Claws of the wolf-tooth type are preferably suitable for a gearbox intended for use on cycles fitted with a pedal set, with or without an electric motor.
• the claws of the sliding gears and of the idler gears of the gear selection system are in the form of studs, preferably with a trapezoidal section.
• Tenon jaws are preferably suitable for a gearbox intended for use on vehicles equipped with a combustion engine and using an engine brake.
• the or both idler pinion(s) of a sub-assembly comprise(s), between the tenon claws, elements in relief.
• Such elements in relief advantageously contribute to the ejection of the slider from the idler gear after clutch release.
• the gearbox comprises an anti-neutral locking system.
• an anti-neutral locking system advantageously makes it possible to block the passage from the first gear ratio to neutral and vice versa. Unblocking is only possible by a voluntary action of a user.
• said gearbox comprises, when a player cooperates with one or two idler gears, spacer elements for maintaining the spacing between said idler gears.
• Such intermediate holding elements advantageously replace the clip grooves, and therefore the clips or circlips, conventionally used.
• the clip grooves made by removing material from the shaft carrying the idler gears, are the source of incipient fracture, weakening said shaft.
• Figure 1 illustrates an electrically assisted bicycle provided with a gearbox of the invention according to a first version, the gearbox being concealed in a protective casing,
• figure 2 represents the electrically assisted bicycle of figure 1, with the visible gearbox,
• FIG. 3 shows an enlarged view of the gearbox of Figure 2
• Figure 4 shows a top view of the gearbox of Figure 3
• Figure 5 shows a cross-sectional view of the gearbox of Figure 4 along line AA
• figure 6 shows a perspective view of a player of a sub-assembly of the gearbox
• figure 7 shows a perspective view of a blade of a fork of a sub-assembly of the gearbox
• FIG. 8 shows a front view of a barrel and its development of the tracks
• figure 9 shows a perspective view of an alternative embodiment of a fork of a sub-assembly of the gearbox
• FIG. 10 shows a side view of the fork of Figure 9
• Figure 11 shows a perspective view of another variant of production of a fork of a sub-assembly of the gearbox
• Figure 12 shows a side view of the fork of Figure 11
• Figure 13 shows a rear view of the fork of Figure 11,
• figure 14 shows a cross-sectional view of the fork of figure 13 along the line AA
• figure 15 shows a perspective view of an alternative embodiment of an idler gear of a sub-assembly of the gearbox
• FIG. 16 represents an exploded view of the idler gear of FIG. 15,
• FIG. 17 shows a perspective view of the gearbox according to the invention, according to a second version,
• figure 18 shows a front view of the gearbox of figure 17, concealed in its protective casings,
• figure 19 shows a top view of the gearbox of figure 18, with the protective casings,
• FIG. 20 shows a side view of the gearbox of figure 18, with the protective casings,
• figure 21 shows a cross-sectional view of the gearbox, with the protective casings of figure 20 along the line AA,
• figure 22 shows a cross-sectional view of the gearbox, with the protective casings of figure 20 along the line BB,
• figure 23 shows a cross-sectional view of the gearbox, with the protective casings of figure 20 along the line CC,
• figure 24 shows an alternative embodiment of a fork of a sub-assembly of the gearbox of figure 17,
• figure 25 shows a perspective view of an alternative embodiment of an idler gear of a sub-assembly of the gearbox of figure 17,
• figure 26 shows a side view of the idler gear of figure 25,
• figure 27 shows a perspective view of a player suitable for coupling with the idler gear of figure 25.
• gearbox 1 according to the invention advantageously allows gear ratio changes without a break in torque, whether on acceleration, by a gear change to a higher gear, or at deceleration, by downshifting and/or downshifting with engine braking.
• the gearbox 1 is suitable for use on cycles fitted with a pedal, with or without an electric motor (of the electrically assisted bicycle type, known by the acronym VAE).
• Figures 1 to 16 illustrate, in a non-limiting way, the use of the gearbox 1 for an electrically assisted bicycle.
• the gearbox 1 is suitable for use on vehicles equipped with a heat engine and using an engine brake, such as for example a kart, a motorcycle, a car.
• Figures 17 to 27 illustrate, in a non-limiting way, the use of the gearbox 1 for a kart engine.
• the gearbox 1 is a six-speed gearbox. Nevertheless, the number of gear ratios does not limit the invention. Thus, it is possible to adapt the gearbox to the desired number of gear ratios, whether this number is even or odd.
• Figures 1 and 2 represent an electrically assisted bicycle 900, more precisely the rear part thereof, on which the gearbox 1 according to the invention is installed.
• the gearbox 1 is intended to be positioned between a rear wheel 901 and an electric motor 902, in connection with a crankset 903.
• gearbox 1 is concealed in a protective casing 904.
• the protective casing 904 has been removed to make said gearbox visible.
• the gearbox 1 is illustrated in detail in Figures 3 to 5.
• Figure 3 shows an enlarged view of the gearbox of Figure 2.
• Figure 4 shows a top view of the gearbox of Figure 3.
• the Figure 5 shows a cross-sectional view of the gearbox of Figure 4 along the line AA.
• the gearbox 1 comprises a first shaft, called primary shaft 10.
• the primary shaft 10 has for axis of rotation, an axis called first axis of rotation 11.
• the primary shaft 10 extends along said first axis of rotation.
• the primary shaft 10 is configured to be driven in rotation around said first axis of rotation.
• the primary shaft 10 is preferably guided in rotation around said first axis of rotation by ball bearings 13 and/or needle bearings 14, arranged for example at the two longitudinal ends of the primary shaft.
• the primary shaft 10 is intended for and configured to be connected to the motor output, most often coaxial with the crankset 903, of the electric-assisted bicycle 900, via a bevel gear with angle transmission.
• the bevel gear with bevel gear is formed for example by a ring gear with bevel teeth 12a and a pinion with bevel teeth 12b, with substantially perpendicular axes, in engagement with each other.
• the bevel gear 12b drives the primary shaft 10 clockwise, when looking in the direction of travel of the electrically assisted bicycle.
• the inter-tooth clearance of the angle bevel gear can be carefully adjusted by means of a needle bearing 15 precisely positioned by the support of a fine-pitch screw 16, as illustrated in Figure 5.
• the gearbox 1 further comprises a second shaft, said secondary shaft 20.
• the secondary shaft 20 has for axis of rotation, an axis called the second axis of rotation 21.
• the secondary shaft 20 extends along said second axis of rotation. spin.
• the secondary shaft 20 is configured to be driven in rotation around the second axis of rotation 21. Said second axis of rotation is preferably distinct from the first axis of rotation 11 .
• the secondary shaft 20 is thus parallel to the primary shaft 10, and not coaxial.
• the secondary shaft 20 is preferably guided in rotation around said second axis of rotation by ball bearings 13 and/or needle bearings 14, arranged for example at the two longitudinal ends of the secondary shaft 20.
• the secondary shaft 20 is intended for and configured to be connected to the rear wheel 901 of the power-assisted bicycle.
• electric 900 A transmission shaft 905 and a bevel gear with bevel gear (visible in Figure 2) allow for example to ensure the connection between the secondary shaft 20 and the rear wheel 901, as illustrated in Figure 1
• the secondary shaft 20 is connected directly to the transmission shaft 905 and the latter is connected to the rear wheel 901 by the bevel gear with bevel gear.
• the secondary shaft can be connected to a pinion cooperating with a chain or a belt, notched or not.
• the secondary shaft 20 is configured to rotate in the opposite direction to that of the primary shaft 10.
• the primary shaft 10 and the secondary shaft 20 are interconnected via gears E1, E2, E3, E4, E5, E6 forming separate speed ratios.
• the number of gears is even.
• the gearbox 1 comprises at least four gears.
• the primary shaft 10 and the secondary shaft 20 are interconnected by six successive gears E1, E2, E3, E4, E5, E6, forming six reports separate speeds.
• Each gear E1, E2, E3, E4, E5, E6 is formed by a toothed wheel, P1, P2, P3, P4, P5, P6, driven in rotation by one of the two shafts, and an idler pinion S1, S2, S3, S4, S5, S6, mounted on the other shaft, which mesh with each other.
• the wheels P1, P2, P3, P4, P5, P6 are aligned next to each other over part of the length of the shaft which carries them.
• the wheels P1, P2, P3, P4, P5, P6 each mesh with one of the idler gears S1, S2, S3, S4, S5, S6 aligned in correspondence over part of the length of the shaft carrying said idler gears.
• Each wheel P1, P2, P3, P4, P5, P6 is in constant mesh with the associated idler gear S1, S2, S3, S4, S5, S6.
• Each wheel P1, P2, P3, P4, P5, P6 is fixedly linked in rotation and in translation to the shaft which carries it.
• Each idler gear S1, S2, S3, S4, S5, S6 is fixedly linked in translation and mounted free in rotation on the shaft which carries it.
• all the wheels P1, P2, P3, P4, P5, P6 are arranged on the primary shaft 10 and all the idler gears S1, S2, S3, S4, S5, S6 are arranged on the shaft secondary 20.
• the idler wheels and pinions have straight teeth.
• the toothed wheels and the idler gears have helical or epicyclic toothing...
• circlips 39 allow the lateral holding of the idler gears on secondary shaft 20.
• Each gear E1, E2, E3, E4, E5, E6 defines a gear ratio with its own gear ratio.
• the first gear ratio has the lowest gear ratio. It is formed by a first wheel P1 and a first idler gear S1.
• the first gear P1 has the smallest pitch diameter among the plurality of gears and the first idler gear S1 has the largest pitch diameter among the plurality of idler gears.
• the second gear ratio has a higher gear ratio than the first ratio, and is formed by a second wheel P2 and a second idler gear S2.
• the third gear ratio has a higher reduction ratio than the second ratio, and is formed by a third wheel P3 and a third idler gear S3.
• the fourth gear ratio has a higher gear ratio than the third gear, and is formed by a fourth wheel P4 and a fourth idler gear S4.
• the fifth gear ratio has a higher gear ratio than the fourth gear, and is formed by a fifth wheel P5 and a fifth idler gear S5.
• the sixth gear ratio which has the highest gear ratio and is formed by a sixth wheel P6 and a sixth idler gear S6.
• the sixth gear P6 has the largest pitch diameter among the plurality of gears and the sixth idler gear S6 has the smallest pitch diameter among the plurality of idler gears.
• Each idler gear S1, S2, S3, S4, S5, S6 comprises at one of its side faces 32, claws 31.
• the claws 31 are made on a side face of the annular element 30 forming said idler gear. Such an embodiment is visible in Figures 4 and 5 for the first, second, third and fourth idler gears SI, S2, S3, S4.
• the claws 31 are made on a flange 33 fixed to a side face 32 of the annular element 30 forming said idler gear. Such an embodiment is visible in Figures 4 and 5 for the fifth and sixth idler gears S5, S6.
• the dogs 31 are in the form of wolf teeth.
• Wolf teeth are in the overall shape of saw teeth with two adjacent sides forming between them an angle less than or equal to 90°.
• the gearbox 1 further comprises sliders C1, C2, C3 and forks F1, F2, F3, adapted to take part in changing the gear ratios.
• a sliding gear C1, C2, C3 is configured to mechanically connect in rotation an idler gear S1, S2, S3, S4, S5, S6 to the shaft that carries it, when engaging a gear ratio.
• a slider C1, C2, C3 is fixedly connected in rotation to the shaft which carries it and movable in translation on said shaft, along the axis of rotation of said shaft, to allow it to be hooked with the adjacent idler gear.
• each slider C1, C2, C3 is configured to be associated with two consecutive idler gears of the same shaft.
• Each slider C1, C2, C3 is thus linked in rotation to the shaft carrying the two idler gears, in the example to the secondary shaft 20, and movable in translation on said secondary shaft, along the second axis of rotation, according to two directions.
• gear ratios are brought together in pairs with a slider C1, C2, C3 which engages on the one hand one of the two associated idler gears by displacement in one direction and on the other hand the other gear crazy by moving in the other direction.
• pairs of idler gears are preferably arranged in such a way as to engage two numerically successive gear ratios with different players.
• the idler gears are successively mounted on the secondary shaft in the following order: S1, S3, S2, S5, S4, S6.
• the wheels are fixed successively on the primary shaft in the following order: P1, P3, P2, P5, P4, P6.
• the gear ratios are therefore in the following order: 1 st , 3 rd , 2 nd , 5 th , 4 th , 6 th . Thanks to this arrangement, it is possible to temporarily engage two successive gears at the same time, so as not to have a break in torque in the transmission of the motor movement.
• the walkmans 01, C2, C3 are three in number in this example and called first, second and third walkman. They are all mounted on the secondary shaft 20 and are respectively positioned between the first and third idler gears S1, S3, the second and fifth idler gears S2, S5 and the fourth and sixth idler gears S4, S6.
• the sliding gears 01, C2 and C3 are used respectively to engage the 1 st and 3 rd gears, the 2 nd and 5 th gears, and the 4 th and 6 th gears.
• Each player C1, 02, 03 comprises an annular element 40 having an internal periphery 41 and an external periphery 42.
• each slider comprises, at the inner periphery 41, longitudinal grooves 41 1 regularly distributed over the circumference of said inner periphery.
• These longitudinal splines 41 1 are intended to cooperate with complementary longitudinal splines (not shown) regularly distributed over the circumference of an outer surface of the secondary shaft 20, at least at the level of a displacement zone of said slider.
• These longitudinal splines 41 1 advantageously allow the translation but block the rotation of the player C1, 02, 03 with respect to the secondary shaft 20 with which it is associated.
• Each player has, at the outer periphery 42, a circular groove 421 intended to receive a fork.
• Each slider comprises, at the side faces 43, dogs 44.
• the dogs 44 of a side face 43 of a player are complementary to the dogs 31 of the idler gear located opposite said side face and are intended to enter into cooperation with said dogs of said idler gear.
• Each player C1, C2, C3 is advantageously able to take at least three different positions: a neutral position and two dogged positions.
• the player In the neutral position, the player is positioned between the two associated adjacent idler gears so that it is clear of the gear ratios.
• the claws 44 of each side face 43 of the slider are positioned at a distance from the claws 31 of each idler gear opposite.
• the slider In a clutched position, the slider is clutched to one of the two associated idler gears, so as to engage the associated gear ratio.
• the slider In the other clutched position, the slider is clutched to the other associated idler gear so as to engage the associated gear ratio.
• the first slider C1 is in the clutched position with the first idler gear S1.
• the second and third players C2, C3 are in neutral position. 1st gear is thus engaged.
• the dogs 44 are in the form of wolf teeth capable of cooperating with the wolf teeth of the associated idler gear.
• the wolf teeth 44 of a side face 43 of a walkman are therefore complementary to the wolf teeth 31 of the associated idler gear.
• the wolf teeth 44 of a side face 43 of a player are inclined so as to produce a one-way freewheel coupling.
• the wolf teeth 31 of the idler gear hook the wolf teeth 44 of a side face 43 of an associated player, causing said secondary shaft to be driven in rotation and escape in the opposite direction, like freewheel pawls.
• the wolf teeth of a sliding gear or an idler gear take the overall form of saw teeth having two adjacent sides making between them an angle less than 90° and an angle a (illustrated in figure 15 for the pinion idler and in Figure 6 for the player) between the side face (referenced 32 for the idler gear and 43 for the player) and a perpendicular to the second axis of rotation 21, less than or equal to 90 °, preferably lower.
• This angle a advantageously determines the coupling bond strength of an idler gear with a player.
• the forks F1, F2, F3 ensure the displacements in translation walkmans C1, C2, C3, a fork cooperating with a walkman.
• a first fork F1 cooperates with the first player C1
• a second fork F2 cooperates with the second player C2
• a third fork F3 cooperates with the third player C3.
• the forks F1, F2, F3 are configured to slide in translation on a guide pin 55.
• Said guide pin is preferably parallel to the primary 10 and secondary 20 shafts, in a non-coaxial manner.
• Said guide pin may for example be a profile such as a rod of circular cross section, as illustrated in Figure 3.
• Each fork F1, F2, F3 preferably comprises, as illustrated in FIG. 7, a blade 50 comprising a body 51 and two branches 52 connected to said body.
• the body 51 of each fork F1, F2, F3 has, in its thickness, a through hole 511 through which the guide pin 55 can pass through.
• the two branches 52 have free ends 521 intended to engage, with play, in the circular groove 421 of the associated player C1, C2, C3.
• Each fork F1, F2, F3 further comprises a core 53 comprising a through bore 531 intended to receive the guide pin 55. Said core and the body 51 of said blade are fixedly linked together.
• the through hole 511 advantageously comprises, as illustrated in FIG. 7, a keying device 512 making it possible to facilitate the assembly of the blade and the core to guarantee their relative positioning and consequently their correct positioning in the gearbox.
• Each fork F1, F2, F3 further comprises a guide finger 54 intended to be linked with a control barrel 60.
• said guide finger of a fork F1, F2, F3 is fixedly attached to core 53.
• guide finger 54 and core 53 form a one-piece assembly.
• the forks F1, F2, F3 are driven in translation along the guide pin 55, via the guide fingers 54, by the control barrel 60.
• the control barrel 60 is for example, as illustrated in FIGS. 3 and 8, an element of generally cylindrical shape, of circular cross-section. Barrel 60 is guided in rotation about an axis called barrel axis 61. Said barrel axis is preferably parallel to the axis of guide 55 of the forks F1, F2, F3.
• Barrel 60 includes guide members. Each guide member is configured to guide a guide finger 54 of a fork F1, F2, F3.
• the guide members are tracks T1, T2, T3.
• Each track T1, T2, T3 is configured to receive a guide pin 54 from a fork F1, F2, F3.
• Each track T1, T2, T3 extending globally over a circumferential surface of barrel 60.
• each track T1, T2, T3 is in the form of a groove made in the barrel, extending from the circumferential surface of the barrel 60.
• the guide members comprise parts, called annular parts A1, A2, A3, attached to the barrel. These annular parts A1, A2, A3 are linked fixedly or not, see monobloc, of the barrel 60.
• the annular parts illustrated in Figures 3-5, 8 are independent of each other.
• Each annular part A1, A2, A3 is for example in the form of an annular element arranged around the barrel.
• Each annular part A1, A2, A3 comprises a track T1, T2, T3.
• Each track T1, T2, T3 extends globally over a circumferential surface of the associated annular part A1, A2, A3.
• each track T1, T2, T3 is in the form of a groove made in the associated annular part A1, A2, A3, extending from the circumferential surface of said annular part.
• barrel 60 comprises three annular parts A1, A2, A3, each annular part A1, A2, A3 comprising a track.
• the annular parts A1, A2, A3 are fixedly connected to the barrel 60.
• barrel 60 has three tracks, one track per guide finger 54 of a fork.
• a first track T1 is thus associated with the first fork F1, a second track T2 with the second fork F2 and a third track T3 with the third fork T3.
• Each track T1, T2, T3 is made up of different sections. Certain sections, called straight sections 62, extend in a plane perpendicular to the barrel axis 61, while other sections, called ramp or cam sections 63, extend in a plane inclined with respect to the axis barrel 61 .
• Each of the tracks T1, T2, T3 advantageously constitutes a guide for the guide finger 64 of the associated fork F1, F2, F3.
• it is the tracks T1, T2, T3 which direct the movement of the guide fingers 54 of the forks F1, F2, F3, therefore the movement of the forks F1, F2, F3 along the guide axis and consequently the movement of the associated players C1, C2, C3.
• the rotation of the barrel 60 around the barrel axis 61 is carried out for example by maneuvering means arranged on the barrel.
• a pulley 68 acting as a capstan, which receives a pair of cables 69 movable in both directions.
• the cables 69 are preferably connected to a speed selector (not shown in the figures) arranged at the level of a handlebar of the electrically assisted bicycle 900, for example.
• the maneuvering means advantageously make it possible to rotate the barrel 60 around the barrel axis 61, in both directions of rotation, with a single command.
• Rotation of said barrel 60 around barrel axis 61 simultaneously brings each fork guide finger 54 into a section of the associated track.
• a guide finger 54 of a fork F1, F2, F3 is located in a straight section 62
• the rotation of the barrel 60 imposes no translational movement of the guide finger 54, and therefore no translation of said fork along of its guide axis.
• a guide finger 54 of a fork F1, F2, F3 is located in a ramp section 63
• the rotation of the barrel 60 by a cam effect, causes a translation of the guide finger 54 and consequently a translation of said fork along its guide axis 12.
• FIG. 8 represents, by way of illustration, a barrel 60 and the flat development of the tracks T1, T2, T3 for a gearbox 1 whose gears are arranged successively as in FIGS. 2 to 4, namely E1, E3, E2, E5, E4 and E6.
• tracks T1, T2, T3 of barrel 60 makes it possible to obtain 6 speed ratios.
• the first track T1 (the leftmost track in Figure 8) allows the translational movement of the first fork F1, via its guide pin 54, and of the first associated player C1, so as to engage the 1st gear ratios or 3rd gear .
• the second track T2 allows the movement in translation of the second fork F2, via its guide finger, and the associated second player C2, so as to engage the 2nd or 5th gear ratios .
• the third track T3 allows the translational movement of the third fork F3, via its guide finger, and of the associated third slider C3, so as to engage the 4 th or 6 th gear ratios.
• the straight section 62 of the first track T1 is offset transversely (to the left in the figure) with respect to a middle position (represented by a first vertical line V1 in FIG. 8) of the first track T1: this means that the first slider C1 is in the dogged position with the first idler gear S1; the third idler gear S3 is free to rotate around the secondary shaft 20,
• the straight section 62 of the second track T2 is located at a middle position (represented by a second vertical line V2 in FIG. 8) of the second track T2: the second player C2 is in the neutral position; the second and fifth idler gears S2, S5 are free to rotate around the secondary shaft 20,
• the straight section 62 of the third track T3 is located at a middle position (represented by a third vertical line V3 in FIG. 8) of the third track T3: the third player C3 is in the neutral position; the fourth and sixth idler gears S4, S6 are therefore free to rotate around the secondary shaft 20.
• the straight sections 62 of the first and third tracks T1, T3 are located at the middle position of their respective tracks: the first and third players C1, C3 are in neutral position; the first, third, fourth and sixth idler gears S1, S3, S4, S6 are therefore free to rotate around the secondary shaft 20,
• the cross section 62 of the second track T2 is offset transversely (to the left in the figure) relative to the middle position of the second track T2: the second sliding gear C2 is dogged with the second idler gear S2; the fifth idler gear S5 is free to rotate around the secondary shaft.
• a section at ramp 63 is inserted between the two straight sections 62 of the first track T1, laterally shifting the guide pin 54 of the first fork F1 and consequently causing the displacement of said first fork F1 and of the first slider C1 towards its neutral position.
• a ramp section 63 is interposed between the two straight sections 62 of the second track T2, laterally shifting the guide finger 54 of the second fork F2 and consequently causing the displacement of said second fork F2 and of the second slider C2 to a dogged position, here with the second idler gear S2.
• the cross section 62 of the first track T1 is offset transversely (to the right in the figure) with respect to the middle position of the first track T1: the first slider C1 is interlocked with the third idler gear S3; the first idler gear S1 is free to rotate around the secondary shaft 20,
• the straight sections 62 of the second and third tracks T2, T3 are located at the middle position of their respective tracks: the second and third players C2, C3 are in neutral position; the second, fourth, fifth and sixth idler gears S2, S4, S5, S6 are therefore free to rotate around the secondary shaft 20.
• the straight sections 62 of the first and second tracks T1, T2 are located at the middle position of their respective tracks: the first and second players C1, C2 are in the neutral position; the first, second, third and fifth idler gears S1, S2, S3, S5 are therefore free to rotate around the secondary shaft 20,
• the straight section 62 of the third track T3 is offset transversely (to the left in the figure) with respect to the middle position of the third track T3: the third player C3 is dogged with the fourth S4 idler gear; the sixth idler gear S6 is free to rotate around the secondary shaft.
• the straight sections 62 of the first and third tracks T1, T3 are located at the middle position of their respective tracks: the first and third players C1, C3 are in neutral position; the first, third, fourth and sixth idler gears S1, S3, S4, S6 are therefore free to rotate around the secondary shaft 20,
• the cross section 62 of the second track T2 is offset transversely (to the right in the figure) with respect to the middle position of said second track T2: the second slider C2 is interlocked with the fifth idler gear S5; the second idler gear S2 is free to rotate around the secondary shaft.
• the straight sections 62 of the first and second tracks T1, T2 are located at the middle position of their respective tracks: the first and second players C1, C2 are in the neutral position; the first, second, third and fifth idler gears S1, S2, S3 and S5 are therefore free to rotate around the secondary shaft 20,
• the cross section 62 of the third track T3 is offset transversely (to the right in the figure) with respect to the median position of said third track T3: the third slider C3 is interlocked with the sixth idler gear S6; the fourth idler gear S4 is free to rotate around the secondary shaft.
• said barrel comprises, at the level of the circumferential surface, an indexing wheel 64.
• This indexing wheel 64 comprises recessed portions 65 Tl regularly spaced around the circumference of said barrel. These recessed portions will be called indexing notches 65.
• indexing notches 65 There are as many indexing notches 65 as gear ratios of the gearbox 1. These indexing notches 65 make it possible to position each fork F1 precisely, F2, F3, and therefore the associated player C1, C2, C3, to engage the gear ratio or put it in neutral.
• the gearbox 1 can also comprise, in addition to the gear ratios, a neutral point.
• This neutral point is characterized by a neutral positioning of all the players C1, C2, C3.
• the indexing wheel 64 of the barrel 60 comprises on the circumference of said barrel, in addition to the indexing notches 65 for each gear of the gearbox, an additional indexing notch for positioning in neutral.
• This additional indexing notch is preferably made between the indexing notch for the 1st gear and the indexing notch for the 6th gear .
• indexing notches 65 are intended to cooperate, for example, with an indexing finger 66 pushed by a spring 66b (visible in FIG. 4) compressed by a stopper 67, adjustable or not, as for example illustrated in the figures 3 and 4.
• the indexing finger 66 is provided with a ball bearing roller 66a advantageously allowing the smoothness and precision of the indexing of the barrel 60 to be optimized.
• said gearbox comprises a means for locking the barrel 60 in rotation.
• This rotation locking means advantageously makes it possible to lock the rotation of the barrel on the notch indexation associated with the breakeven point.
• the crankset spins in a vacuum.
• Such locking means form an anti-theft device for the bicycle.
• this blocking means is a mechanical system, preferably actuated by a key.
• this blocking means is a mechatronic system, preferably actuated by a remote control or a smartphone.
• a subassembly is formed by a fork, the sliding gear, the idler gear and the associated guide member.
• one of the elements of each subset comprises an elastic return means.
• Such an elastic return means advantageously makes it possible to delay the operation of clutching a gear ratio and the operation of disengaging another gear ratio, during a gear change.
• the fork F1, F2, F3 comprises the elastic return means.
• the fork F1, F2, F3 comprises the elastic return means.
• the blade 50 of the fork forms the elastic return means. Said blade is thus configured to deform elastically.
• Said blade is for example a flexible blade. At rest, that is to say without stress exerted on it, the blade 50 of the fork F1, F2, F3 extends in a plane substantially perpendicular to the guide axis 55. Under stress, the blade 50 flexes so that it no longer extends in a plane substantially perpendicular to the guide axis.
• Said flexible blade can for example be made of a spring steel sheet material.
• the flexible blade of the fork F1, F2, F3 may have, on each of the faces 56 of the flexible blade, and at the level of the free ends 521 of each branch 52, a protuberance 522, for example in hemispherical dome shape.
• protuberances 522 advantageously make it possible to reduce the contact zone of the fork with the walls 422 of the circular groove 421 of the associated slider, on which said fork can momentarily exert lateral pressure.
• the flexible blade because of its elasticity, advantageously makes it possible to delay the dog clutch or the unclutch of a player with an idler gear during a gear change, as will be explained later in an example of operation.
• a fork F1, F2, F3 may comprise two flexible blades 50, which are substantially identical and parallel, which together act as elastic return means.
• Such a fork F1, F2, F3 advantageously makes it easier to differentiate between the force of introduction of the player C1, C2, C3 associated with the idler gear and the force of extraction of said player from the idler gear.
• the two flexible blades 50 are preferably spaced apart by a spacer element 57, as shown in Figure 10.
• each flexible blade 50 of the fork F1, F2, F3 may have, on a face 56 facing one of the walls 422 of the circular groove 421 of the associated player, and at the free ends 521 of each branch 52, a protuberance 522, for example in the shape of a hemispherical dome.
• Such a fork can be mechanically assembled as follows: the core 53, a washer 58, a first flexible blade 50, the spacer element 57, a second flexible blade 50, another washer 58 then a nut 59 configured to tighten all the parts forming the fork F1, F2, F3 together.
• Each of said parts has an orifice for the passage of the guide pin.
• washers 58 are lug washers.
• the wing washers advantageously make it possible to differentiate the elastic force for the introduction of the associated sliding gear into the idler gear and the elastic force for extracting said sliding gear from the idler gear.
• the length and shape of said ears of a washer have an influence on the quality of elasticity of the fork.
• the guide member is either a track T1, T2, T3 extending over the circumferential surface of the barrel or an annular part A1, A2, A3 comprising a track T1, T2, T3 extending on the circumferential surface of the annular piece A1, A2, A3, said annular piece being fixedly connected to the barrel, or integral with the barrel.
• the movement of the guide finger directly drives the fork, in particular the blade 50, independently of the elastic return means.
• the elastic return means for each subassembly, is a flexible blade 50 of the fork. It is clear that the operation of the gearbox 1 described below can be transposed to any other elastic return means. Similarly, the elastic return means used in each subassembly may be different. In this example, the player cooperates with two idler gears.
• the gearbox 1 is for example in 1st gear.
• the first player C1 is dogged with the first idler gear S1
• the second and third players C2, C3 are in neutral position.
• the cyclist manipulates the selector, located on the handlebars.
• the selector acts on the barrel 60, via the maneuvering means.
• the barrel 60 then turns in rotation until the indexing finger 66 is positioned in an indexing notch 65 of the indexing wheel 64 of the barrel 60 corresponding to the 2nd gear.
• the guide finger 54 of the second fork F2 follows the second track T2, moving the said second fork F2 in translation on the guide pin 55, to move the second slider C2 in translation towards the second idler gear S2 until dog clutching ,
• the guide finger 54 of the first fork F1 follows the first track T1, moving the said first fork F1 in translation on the guide shaft, to move the first slider C1 in translation and bring it back to neutral,
• the second slider C2 is moved in translation towards the second idler gear S2.
• two integral parts or two integrally linked/interconnected parts is meant two mechanically linked parts allowing at least one degree of freedom.
• the blade 50 of the second fork F2 will automatically return to its state at rest, exerting a pressure force on the second sliding gear C2 to push it laterally towards the second idler gear S2, causing the second sliding gear C2 to dog clutch with the second idler gear S2 and engage the 2 th speed.
• the guide finger 54 of the first fork F1 is moved in translation, driving said first fork in translation to move the first player C1 in translation towards its neutral position.
• the blade 50 of the first fork F1 thanks to its elasticity, will bend and find itself under stress.
• the idler gear of the 1st gear will start to turn slower than the secondary shaft 20 which carries it and the pressure on the first slider S1 will then be released.
• the dogs 44 of said first slider C1 and the dogs 31 of the first idler gear S1 then uncouple naturally.
• the blade 50 of the first fork F1 thanks to its elasticity, will then automatically return to its state at rest, exerting a restoring force on the first slider C1 to bring it back to its neutral position after clutch release with the first idler gear S1.
• the elasticity of the blade 50 of the first fork F1 thus allows the first slider C1 which must be uncoupled from the first idler gear S1 to return to its neutral position, to wait for the pressure on said first idler gear S1 to be released, to gently, effortlessly and naturally.
• Such a gearbox 1 according to the invention via the elasticity of the blade 50 of the forks F1, F2, F3, advantageously makes it possible to program the engagement of one gear and the disengagement of the other gear simultaneously.
• the gearbox 1 according to the invention thanks to the elasticity of the blade 50 of the forks, advantageously allows, for a very short time, of the order of a thousandth of a second for example, the simultaneous engagement of two successive speeds.
• the guide finger 54 oscillates around an axis called the pivot axis 542, an axis perpendicular to the guide axis 55.
• the guide axis preferably extends in a plane substantially formed by the blade 50 of the fork, when the associated player is in neutral position.
• the so-called oscillating guide finger 54 is preferably partly housed in the core 53 of the fork. Core 53 thus advantageously serves as a support for said pivot pin.
• the core 53 further comprises a slot 532 for the passage of the guide finger 54.
• Said slot has a dimension greater than the dimension, in cross section, of the guide finger 54 to allow the movement of said guide finger in said slot.
• the springs 541 On either side of the guide finger 54, in the core 53, are arranged the springs 541. At rest, or in a state of minimum stress, the springs 541 maintain the guide finger 54 centered in the slot 532 of the core.
• the guide finger 54 cooperates with the fork F1, F2, F3, the pivoting of the guide finger causing the lateral displacement of the fork.
• the blade 50 of said fork is a rigid blade.
• the blade 50 can be integral with the core 53 or be fixedly connected to the core 53.
• the guide member is either a track T1, T2, T3 extending over the circumferential surface of the barrel or an annular part A1, A2, A3 comprising a track T1, T2, T3 extending on the circumferential surface of the annular part A1, A2, A3, said annular part being fixedly connected, or in one piece, to the barrel.
• the elastic return means is the same for each subset. Similarly, the elastic return means used in each sub-assembly may be different.
• the player cooperates with two idler gears.
• the player and the two idler gears do not include elastic return means.
• Gearbox 1 is for example in 2nd gear.
• the second player C2 is dogged with the first idler gear S2, and the first and third players C1, C3 are in neutral position.
• the cyclist manipulates the selector, located on the handlebars.
• the selector acts on the barrel 60, via the maneuvering means.
• the barrel 60 then turns in rotation until the indexing finger 66 is positioned in an indexing notch 65 of the indexing wheel 64 of the barrel corresponding to the 3 rd gear.
• the guide finger 54 of the first fork F1 follows the first track T1, moving the first fork F1 in translation, and its core 53, on its guide pin 55, to move the first slider C1 in translation towards the third idler gear S3 until dog clutching,
• the guide pin 54 of the second fork F2 follows the second track T2, moving the second fork F2 in translation, and its core 53, on the guide pin 55, to move the second slider C2 in translation and bring it back to the neutral,
• the first slider C1 is moved in translation towards the third idler gear S3.
• the translation of the second slider C2 is temporarily blocked, simultaneously blocking the translation of the second fork F2 and of its core 53 on the guide pin 55.
• the guide finger 54 of the second fork F2 which continues to follow the second track T2, shifting into the slot 532 of the core 53, and compressing one of the springs 541 in said core, which then finds itself temporarily under stress.
• the compressed spring due to its elasticity, will automatically return to its rest state, causing the movement of the core 53 of the second fork F2 along the guide pin 55, therefore the movement of the blade 50 of the second fork F2 and the second associated player C2.
• the second slider C2 is thus moved laterally from the second idler gear S2 and returned to its neutral position after being released from the second idler gear S2.
• the elasticity of the spring in the core of the second fork F2 thus allows the second slider C2 which must be uncoupled from the second idler gear S2 to return to its neutral position, to wait for the pressure on said second idler gear S1 to be released, gently, effortlessly and naturally.
• each idler gear S1, S2, S3, S4, S5, S6 comprises the elastic return means.
• each idler gear comprises the elastic return means.
• An idler gear comprises, as illustrated in figures 15 and 16:
• an outer part 35 in the form of an annular element, comprising an inner periphery 351, an outer periphery 352, and a lateral face called support 353,
• the internal periphery 351 of the external part 35 comprises longitudinal grooves 354.
• the central part 34 comprises, at an outer periphery 342, longitudinal grooves 344 complementary to the longitudinal grooves 354 of the inner periphery 351 of the outer part 35, to advantageously ensure the connection in rotation of said central part with the outer part , while allowing translational movement of said central part in/out of the outer part, along the second axis of rotation 21 .
• the central part 34 comprises, at an internal periphery 341, a slide bearing receiving the secondary shaft 20 and allowing said idler gear to rotate freely on said secondary shaft.
• the central part 34 comprises, at the level of a lateral face, the claws 31 .
• the spring 36 forms the elastic return means.
• the spring 36 is preferably a spring working in tension or in compression, depending on the stresses.
• the spring 36 can be fixedly linked by one end to the outer part 35, preferably to the lateral bearing face 353, and by an opposite end, to the central part 34.
• FIG. 15 is a perspective view of the idler gear assembled, in its position at rest or when it is clutched before a player.
• Retaining elements are configured to prevent the lateral displacement of the central part 34 out of the outer part 35.
• Such retaining elements are for example positioned between the outer part 34 and the central part 34 or between the central 34 and secondary shaft 11 .
• each slider C1, C2, C3 comprises the elastic return means instead of the idler gear.
• the player comprises an outer part, a central part intended to be inserted into the outer part and a spring intended to be inserted between the central part and a bearing face of the outer part.
• the blade 50 of said fork is a rigid blade.
• the blade 50 can be integral with the core 53 or be fixedly connected to the core 53.
• the guide finger 54 is not an oscillating guide finger.
• the guide member is either a track T1, T2, T3 extending over the circumferential surface of the barrel or an annular part A1, A2, A3 comprising a track T1, T2, T3 extending over the circumferential surface of the annular part A1, A2, A3, said annular part being fixedly connected, or in one piece, to the barrel 60.
• the movement of the guide finger directly drives the fork, in particular the blade 50, independently of the elastic return means.
• the player cooperates with two idler gears.
• the player and the two idler gears do not include elastic return means.
• This example of operation can be transposed to the case where it is the player which includes the elastic return means.
• Gearbox 1 is for example in 3 rd gear.
• the cyclist manipulates the selector, located on the handlebars.
• the selector acts on the barrel 60, via the maneuvering means.
• the barrel 60 then turns in rotation until the indexing finger 66 is positioned in an indexing notch 65 of the indexing wheel 64 of the barrel corresponding to the 4th gear .
• the guide finger 54 of the first fork F1 follows the first track T1, moving the first fork F1 in translation on the guide pin 55, to move the first slider C1 in translation and bring it back to neutral,
• the third slider C3 is moved in translation towards the fourth idler gear S4.
• the guide finger 54 of the first fork F1 is moved in translation, driving said first fork F1 in translation to move the first player C1 in translation towards its neutral position.
• the central part 54 of the third idler gear S3 is driven laterally with the first slider C1, causing a slight stretching of the spring 36.
• the spring 36 will then automatically return to its state at rest, exerting a restoring force on the central part 34 of the third idler gear S3 to move it away from the first slider C1 and bring it back into the outer part 35 of said third idler gear S3.
• the first player becomes free to rotate relative to the secondary shaft.
• the guide member comprises the elastic return means.
• each guide member comprises the elastic return means.
• the guide member comprises an annular part A1, A2, A3 attached to the barrel 60.
• the annular part A1, A2, A3 comprises a track T1, T2, T3 extending over the circumferential surface of said annular piece. Said annular part is only linked in rotation to the barrel 60 and free in translation over a predefined distance.
• the guide member comprises a spring (not shown in the figures) arranged against the annular part A1, A2, A3, at a side face. Said spring is for example connected, by one end, to the annular part and, by another end, to a stop, fixedly connected to the barrel.
• the spring forms the elastic return means.
• the spring At rest, or in a state of minimal stress, the spring maintains the annular part in a position such that the straight sections of the track are arranged so that the slider is either in the neutral position, or clutched with one of the pinions. crazy.
• the blade 50 of said fork is a rigid blade.
• Blade 50 may be integral with core 53 or be fixedly attached to core 53.
• Guide finger 54 is not an oscillating guide finger.
• the guide member comprises at least two springs.
• Each spring is arranged on either side of the annular part, at opposite side faces of said annular part.
• Each spring is connected, by one end, to said annular part and, by another end, to a fixed stop on barrel 60. Said at least two springs form the elastic return means.
• the movement of the guide finger directly drives the fork, in particular the blade 50, independently of the elastic return means.
• the elastic return means is the same for each subset. Similarly, the elastic return means used in each sub-assembly may be different.
• the player in each sub-assembly, the player cooperates with two idler gears.
• the player and the two idler gears do not include elastic return means.
• Gearbox 1 is for example in 2nd gear.
• the second player C2 is dogged with the first idler gear S2, and the first and third players C1, C3 are in neutral position.
• the cyclist manipulates the selector, located on the handlebars.
• the selector acts on the barrel 60, via the maneuvering means.
• the barrel 60 then turns in rotation until the indexing finger 66 is positioned in an indexing notch 65 of the indexing wheel 64 of the barrel corresponding to the 3 rd gear.
• the guide finger 54 of the first fork F1 follows the first track T1, moving the first fork F1 in translation, and its core 53, on its guide pin 55, to move the first slider C1 in translation towards the third idler gear S3 until dog clutching,
• the guide pin 54 of the second fork F2 follows the second track T2, moving the second fork F2 in translation, and its core 53, on the guide pin 55, to move the second slider C2 in translation and bring it back to the neutral,
• the first slider C1 is moved in translation towards the third idler gear S3.
• the guide finger 54 of the second fork F2 is moved in translation, driving said fork in translation to move the second player C2 in translation towards its neutral position.
• the translation of the second slider C2 is temporarily blocked, simultaneously blocking the translation of the second fork F2 and of its core 53 on the guide pin 55.
• the guide finger 54 of the second fork F2 continuing to follow the second track T2 , causes an offset of the annular part A2, either stretching or compressing the spring. Said spring is then temporarily under stress.
• the spring due to its elasticity, will automatically return to its resting state, causing the annular part A2 to move on the barrel 60, along the barrel axis, and consequently driving the core 53 of the second fork F2 the along the guide axis 55, therefore the displacement of the blade 50 of the second fork F2 and of the associated second player C2.
• the second slider C2 is thus moved laterally from the second idler gear S2 and returned to its neutral position after being released from the second idler gear S2.
• the elasticity of the spring in the core of the second fork F2 thus allows the second slider C2 which must be uncoupled from the second idler gear S2 to return to its neutral position, to wait for the pressure on said second idler gear S1 to be released, gently, effortlessly and naturally.
• Figures 17 to 27 show the gearbox 1 suitable for use on a vehicle equipped with a heat engine where the engine brake is used.
• this vehicle is a kart.
• Figure 17 shows a perspective view of said gearbox.
• the gears E1, E2, E3, E4, E5, E6, comprising the cogwheels P1, P2, P3, P4, P5, P6 fixedly linked, in rotation and in translation, to the primary shaft 10 and the idler gears S1 , S2, S3, S4, S5, S6 fixedly linked, in translation, to the secondary shaft 20; in the example, the gears are also 6 in number,
• each guide member is either a track extending over the circumferential surface of the barrel or an annular part A1, A2, A3 comprising a track T1, T2, T3 extending over the circumferential surface of the annular part, said annular part being fixedly linked, or one-piece, to the barrel; the guide fingers 54 of the forks F1, F2, F3 are each inserted respectively into one of the tracks T1, T2, T3.
• the primary shaft 10 is intended for and configured to be connected to a clutch system (not shown).
• the idler gears are this time mounted successively on the shaft secondary in the following order: S1, S4, S5, S3, S6, S2.
• the wheels are fixed successively on the primary shaft in the following order: P1, P4, P5, P3, P6, P2.
• the gear ratios are therefore in the following order: 1 st , 4 th , 5 th , 3 rd , 6 th , 2 nd .
• the players C1, C2, C3 are now respectively positioned between the first and fourth idler gears S1, S4, the fifth and third idler gears S5, S3 and the sixth and second idler gears S6, S2.
• the first, second and third sliding gears C1, C2, C3 enable respectively to engage the 1 st and 4 th gears, the 5 th and 3 rd gears, and the 6 th and 2 nd gears.
• Figures 18 to 23 represent the protective casings 80 of a low kart engine inside which is installed the gearbox 1 according to the second version.
• the release axis 82 of the lever clutch 81 comprises, in a conventional manner, at its lower end, a cam which pushes the clutch rod, advantageously allowing the separation of clutch discs (not shown).
• Figures 21 to 23 respectively show a cross-sectional view of the gearbox, surrounded by its protective casings 80, of Figure 20 along line AA, BB and CC.
• spacer pieces 83 are disposed between the wheels of the gears. These spacer pieces 83, three in number, are arranged respectively between the first and fourth wheels P1, P4, the fifth and third wheels P5, P3, and the sixth and second wheels P6, P2. These spacer pieces 83 advantageously make it possible to space the wheels, so that they can face the associated idler gears, idler gears spaced out for moving the players C1, C2, C3.
• the idler gear is an annular element 30 comprising, on one side face, a needle thrust bearing 85 and at its internal periphery, a needle bearing 14 which rotates on a stepped bearing 86 to laterally retain the idler gear on the player side.
• Said bearing is preferably smooth on the outside and fluted on the inside.
• Said bearing further comprises housings, for example three housings distributed every 120°, intended to receive the ends of cylindrical needles 86a. These cylindrical needles 86a are for example embedded in certain longitudinal splines of the secondary shaft 20.
• the cylindrical needles 86a advantageously make it possible to control the precise spacing between two idler gears sharing the same player which therefore slides on these cylindrical needles 86a.
• These cylindrical needles form intermediate elements for maintaining the spacing between said two idler gears.
• Said cylindrical needles advantageously replace the clip grooves conventionally used, causing incipient breakage, risk factors for breakage of the shaft carrying the idler gears, here the secondary shaft.
• the side chain of the stack, on the secondary shaft 20, of the shim washers 84, bearings 86, and cylindrical needles 86a allows a minimum play, or even zero, with the ball bearings 13 located at the ends of the said secondary shaft.
• the dogs 31 are lugs of the tenon type.
• the posts have a trapezoidal section, with the small base of the tenons located on the side of the side face 32 of the idler gear.
• the idler gear dogs 31 include:
• this angle P is of the order of 85° ⁇ 5°
• the large base of the dog clutch 31 of the idler gear advantageously makes it possible to guarantee the ejection of the player cooperating with said idler gear, during a gear change, for the ejected gear ratio.
• elements in relief 38 are arranged concentrically between the claws 31 of the idler gear.
• Such elements in relief 38 can be of substantially the same height or less than the height of the claws 31 of the idler gear.
• These elements in relief 38 are in the overall form of a V-shaped roof, symmetrical or not, having two adjacent sides making between them an angle greater than 90°. The adjacent sides advantageously help the blade 50 of the fork to eject the player when changing gears.
• these elements in relief can be positioned on the slider C1, C2, C3 instead of the idler gear.
• the claws 44 of said player C1, C2, C3 have first 441 and second sides 442 having a complementary shape respectively to the first 311 and second 312 sides of the dogs 31 of the idler gear with which it cooperates.
• certain projecting parts of the longitudinal splines 411 have disappeared and are replaced by three hollow longitudinal housings 45, intended to allow the passage of the cylindrical needles 86a.
• These housings 45, three in number in FIG. 27, are preferably made by removing material.
• barrel 60 is guided in rotation around its barrel axis 61 by ball bearings 13, in the example located at the two ends of the barrel.
• the barrel axis 61 is configured to receive a mechanism suitable for cooperating with a manual or pedestrian lever of the kart gear selector.
• the gearbox 1 advantageously comprises, in addition to the 6 gear ratios, a dead point.
• This neutral point is characterized by a neutral positioning of all the players C1, C2, C3.
• the indexing wheel 64 of the barrel comprises on the circumference of said barrel, in addition to the indexing notches 65 for each gear of the gearbox, an additional indexing notch for positioning in neutral.
• This additional indexing notch is preferably made between the indexing notch for the 1st gear and the indexing notch for the 6th gear .
• all the indexing notches 65 cooperate, preferentially, with an indexing pin 66 pushed by a spring compressed by a cap, as for example illustrated in figure 24.
• said gearbox comprises an anti-neutral locking system 70.
• the anti-neutral locking system 70 comprises a locking rod 71, as shown in Figure 17.
• the locking rod is preferably pushed by a spring 72 against a cam (kind of spin) made in the axis 82 of disengagement .
• This additional cam opposite the conventional cam which actuates the clutch rod advantageously makes it possible to raise said locking rod 71 under the action of said spring.
• the clutch lever 81 actuates a cable connected to the indexing finger 66.
• said cable pulls on the indexing finger, which brings it out of a deeper zone in the notch of 1st gear and which blocks its rotation only towards neutral, then when neutral is selected, falls back into an indexing notch similar to that of 1 st gear to block neutral, unless the driver disengages.
• the anti-neutral locking system 70 is a mechanical system. It is possible, without departing from the framework of the invention, to produce an anti-neutral locking system in whole or in part mechanical, hydraulic, pneumatic, electromagnetic, etc. and which is operable in a synchronized manner and therefore simultaneously with the clutch system (lever, pedal, lever, etc.), or completely independent of said clutch system.
• the gear selection system is still made up of all the forks, sliding gears, idler gears and gearbox barrel guide components, as for the first version.
• a sub-assembly is formed by a fork, the slider, the two idler gears and the associated guide member.
• a subassembly is formed by a fork, the sliding gear, the idler gear and the associated guide member.
• the blade 50 of the fork of a sub-assembly forms the elastic return means.
• the blade is thus configured to deform elastically.
• said blade is for example a flexible blade.
• the blade 50 of the fork F1, F2, F3 extends in a plane substantially perpendicular to the guide axis 55.
• the blade 50 flexes so that it no longer extends in a plane substantially perpendicular to guide pin 55.
• Said flexible blade can for example be made of a spring steel sheet material. It can also be made of a composite material, such as for example carbon, or any other material having a relatively high elastic limit.
• the flexible blade is made of a material having a bending in the elastic limit corresponding substantially to a height of the claws plus a minimum millimeter.
• the free ends 521 of the branches 52 of the blade 50 of a fork each comprise a clevis 523.
• Each clevis 523 can be fixed at the level of the free end 521 of a branch 52 by a screwing element 524, such as for example a screw or a rivet.
• Each yoke 523 has a bore 526 for receiving a friction pad 525. Said friction pad can rotate freely in rotation around a longitudinal axis of the bore 526 of the yoke.
• the friction pad 525 is intended to cooperate with the circular groove 421 of the associated slider C1, C2, C3.
• the friction pad 525 may have, in section in a substantially radial plane relative to the associated slider, the shape of a cup whose lateral sides 525a come into frictional contact with the corresponding walls 422 of the circular groove. 421 of the associated walkman.
• the core 53 of the fork F1, F2, F3 can indifferently carry, directly or in an attached manner, the guide finger 54 intended to cooperate with one of the tracks T1, T2, T3 of the barrel 60.
• the tightening of the flexible blade 50 on the core 53 can be made by a nut.
• fork F1, F2, F3 is perfectly suited for gearboxes 1 used on vehicles equipped with a thermal engine, whose primary 10 and secondary 20 shafts rotate at speeds much higher than those of a classic bicycle and an electrically assisted bicycle.
• the speed curve of a vehicle equipped with the gearbox according to the invention advantageously presents at each change of higher gear a positive peak (which results in an increase in speed) due to the recovery of the inertial kinetic energy of the engine, whereas with a traditional gearbox this peak is negative (which results in a slight loss of speed).
• the gearbox can advantageously meet the constraints of integration into existing housings, in particular in terms of size, dimensioning (for example, the center distance between the first axis of rotation and the second rotation axis).
• a gearbox can thus be sold as an accessory to replace a traditional gearbox, preferably on motorcycles and karts. This possibility of replacement is particularly interesting in sports disciplines where the casings are approved for several years.

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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)
• General Details Of Gearings (AREA)

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• 2020
  • 2020-10-02 FR FR2010096A patent/FR3114852B1/fr active Active
• 2021
  • 2021-09-30 EP EP21786203.6A patent/EP4200540A1/de active Pending
  • 2021-09-30 US US18/697,181 patent/US20250042506A1/en not_active Abandoned
  • 2021-09-30 CN CN202180104401.XA patent/CN118284755A/zh active Pending
  • 2021-09-30 WO PCT/EP2021/076932 patent/WO2022069622A1/fr not_active Ceased

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