WO2023222260A1 - Dispositif de changement de vitesse de jeu de pédalier avec dispositif de changement de vitesse pour une bicyclette, et bicyclette comprenant un tel dispositif de changement de vitesse de jeu de pédalier - Google Patents

Dispositif de changement de vitesse de jeu de pédalier avec dispositif de changement de vitesse pour une bicyclette, et bicyclette comprenant un tel dispositif de changement de vitesse de jeu de pédalier Download PDF

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Publication number
WO2023222260A1
WO2023222260A1 PCT/EP2023/051076 EP2023051076W WO2023222260A1 WO 2023222260 A1 WO2023222260 A1 WO 2023222260A1 EP 2023051076 W EP2023051076 W EP 2023051076W WO 2023222260 A1 WO2023222260 A1 WO 2023222260A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
bottom bracket
shaft
switching
switching device
Prior art date
Application number
PCT/EP2023/051076
Other languages
German (de)
English (en)
Inventor
Karlheinz Nicolai
Original Assignee
Karlheinz Nicolai
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Karlheinz Nicolai filed Critical Karlheinz Nicolai
Publication of WO2023222260A1 publication Critical patent/WO2023222260A1/fr

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Classifications

    • 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
    • B62M25/08—Actuators for gearing speed-change mechanisms specially adapted for cycles with electrical or fluid transmitting systems
    • 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
    • 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
    • F16H3/083—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 radially acting and axially controlled clutching members, e.g. sliding keys
    • 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
    • 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
    • F16H35/00—Gearings or mechanisms with other special functional features
    • F16H35/008—Gearings or mechanisms with other special functional features for variation of rotational phase relationship, e.g. angular relationship between input and output shaft
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/32—Electric motors actuators or related electrical control means therefor
    • 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
    • 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
    • B62M9/00—Transmissions characterised by use of an endless chain, belt, or the like
    • B62M9/16—Tensioning or adjusting equipment for chains, belts 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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/06—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with parallel axes
    • F16H1/10—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with parallel axes one of the members being internally toothed
    • 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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
    • F16H1/22—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • F16H2055/178—Toothed wheels combined with clutch means, e.g. gear with integrated synchronizer clutch
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02034—Gearboxes combined or connected with electric machines
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F16H57/022—Adjustment of gear shafts or bearings
    • F16H2057/0227—Assembly method measuring first tolerances or position and selecting mating parts accordingly, e.g. special sized shims for transmission bearings
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H2061/2892—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted other gears, e.g. worm gears, for transmitting rotary motion to the output 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
    • 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
    • F16H2063/3093—Final output elements, i.e. the final elements to establish gear ratio, e.g. dog clutches or other means establishing coupling to shaft
    • 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
    • F16H27/00—Step-by-step mechanisms without freewheel members, e.g. Geneva drives
    • F16H27/04—Step-by-step mechanisms without freewheel members, e.g. Geneva drives for converting continuous rotation into a step-by-step rotary movement
    • F16H27/10—Step-by-step mechanisms without freewheel members, e.g. Geneva drives for converting continuous rotation into a step-by-step rotary movement obtained by means of disengageable transmission members, combined or not combined with mechanisms according to group F16H27/06 or F16H27/08
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/02004—Gearboxes; Mounting gearing therein the gears being positioned relative to one another by rolling members or by specially adapted surfaces on the gears, e.g. by a rolling surface with the diameter of the pitch circle
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • 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
    • F16H63/38—Detents

Definitions

  • the invention relates to a bottom bracket circuit with a switching device for a bicycle and a bicycle with such a bottom bracket circuit with a switching device.
  • bottom bracket circuit with a switching device
  • this also means a switching device for a bottom bracket circuit.
  • bottom bracket gear, bottom bracket gear, multiple gear or gear unit are often used in the literature and patents for the same thing.
  • clutch device and switching device are also often used in the literature and patent specifications for the same thing.
  • the auxiliary drive of the electric bicycles considered here is located near the bottom bracket.
  • derailleur gears or hub gears are usually used because there is not enough space at the bottom bracket.
  • derailleur gears are disadvantageous in that the components of the gear shift, namely the sprockets on the rear hub, the at least one chainring and the chain and the chain derailleur are unprotected and therefore easily dirty. A derailleur gear is therefore comparatively maintenance-intensive.
  • a structure of the manual transmission according to EP1445088A2 is advantageous.
  • This is a transmission unit of a vehicle powered by muscle power, with a first shaft, which is usually arranged parallel to the bottom bracket shaft and on which a plurality of idler gears are mounted, and a corresponding number of gears, which are mounted on at least one second shaft , wherein the idler gears can each be connected to the first shaft by means of coupling means, the first shaft being designed as a hollow shaft and having one or two coaxially internal switching pins, characterized in that the switching pin or pins is or are connected to drive means which are designed for this purpose to move the switching bolt(s) axially.
  • the first wave is also often called the switching wave.
  • the coupling means also often called switching clutches or switching means, are designed as positive freewheels and are arranged on axially displaceable switching pins. Freewheel bodies are therefore arranged on the switching pins.
  • a torque which is introduced by the cyclist onto the gearbox while driving and also during the switching process, must be transmitted from the shaft via the coupling means into the respective gear. Shifting under load is very difficult with this type of manual transmission, since the more torque the driver introduces, the more difficult it is for the axial movement of the clutch means to occur.
  • the cause is the increased surface pressure between the force-transmitted components.
  • each individual idler gear can be coupled to the shift shaft with the help of one freewheel tooth, which is movably arranged on the shift shaft.
  • the freewheel teeth are constantly pressed by springs towards the clutch teeth of the idler gears.
  • the geometry of the freewheel teeth is chosen so that they remain reliably engaged in the clutch teeth of the idler gear under load and no reaction force is created in the direction of the actuating means during operation.
  • the actuating means which in this design rotates within the switching shaft as a camshaft, must release the relevant freewheel tooth from its positive locking position when shifting under load and thereby overcome enormous frictional forces.
  • the switching force increases when the user feeds increased torque into the bottom bracket shaft via the pedals. This can be seen as a disadvantage.
  • the actuation means is usually operated by the human hand on the handlebars of the bicycle.
  • actuation by electrical actuators is also common. Since the human hand and small electric motors, such as those used in actuators, can only perform a limited amount of mechanical work, there is a need for a bottom bracket circuit with low switching forces and improved power shifting behavior.
  • the coupling means have a freewheeling function and can be controlled from the outside by an actuating means.
  • This bottom bracket gear is characterized in that the state of at least two coupling means changes simultaneously during the switching process. Controlling the change in the state of the clutch means during the switching process so that idling does not occur is achieved in this way.
  • the coupling means are controlled by rotation of the actuating means. Since the actuating means is located on a shaft that rotates while driving, the switching command must be transmitted from the stationary housing to the rotating shaft using a superposition gear. If the superposition gear, which is usually designed as a planetary gear, is located coaxially and laterally next to the switching shaft, the overall width of the gear increases disadvantageously.
  • stepping gears For example, a mechanical input movement is divided into two output movements with different timing.
  • An axially particularly space-saving stepping gear from Siemens is known, for example, from patent DE1113618.
  • Electric bicycles without bottom bracket shifting according to the state of the art have enough space in their housing to accommodate a torque sensor and a speed sensor.
  • the sum of all sensors and electronic components used within an electric bicycle with an auxiliary drive, especially in the form of a mid-engine, to generate signals which are required to control or regulate the motor in the manner desired by the user, are referred to below as a sensor arrangement.
  • an advantageous embodiment of the bottom bracket circuit is characterized, which has any combination of the following features: a) the switching shaft has two or more than two chambers, which are arranged parallel or almost parallel to the axis of the switching shaft, b) the two or more than two chambers of the switching shaft are not designed coaxially to the axis of the switching shaft, c) there is at least one pivoting support within at least two chambers, d) a pivoting support can assume a first state in which the pivoting support is directly or indirectly connected is connected to at least one coupling body, e) whereby in this first state this coupling body can be brought into a force-transmitting connection to an idler gear, f) where the lateral surface of the switching shaft has depressions in which coupling bodies are located, g) where at least two depressions each have at least one opening with at least one chamber connected is.
  • the bottom bracket circuit is characterized in that a pivotable support can assume a second state in which the pivotable support is not connected to a clutch body or the contact is only almost powerless and in this second state Clutch body cannot be brought into force-transmitting connection to an idler gear.
  • a pivotable support can assume a second state in which the pivotable support is only in light contact with a coupling body without great force and in this second Condition of this clutch body cannot be brought into a force-transmitting connection to an idler gear.
  • the bottom bracket circuit in particular for a vehicle powered by muscle power with an electric auxiliary drive, is characterized in that a first sub-transmission and a second sub-transmission are connected in series for power transmission, the first sub-transmission and the second sub-transmission having a shift shaft on which a plurality are mounted by idler gears, which form wheel pairs of the respective partial transmission with a corresponding plurality of gears, the idler gears being connectable to the shift shaft by means of coupling bodies, then a large number of gears can be achieved with just a few gears.
  • the bottom bracket circuit is equipped with a switching device, characterized in that the shift shaft is designed on its cylindrical lateral surface with several grooves in which almost annular spiral springs are inserted, with the almost annular spiral springs in contact with the coupling bodies.
  • the bottom bracket circuit with a switching device is characterized in that the pinions of at least two pivotable supports are in connection with an actuating gear, the actuating gear being arranged coaxially and rotatably to the switching shaft and the actuating gear being designed with external teeth and internal teeth, so the simultaneous actuation of several pivoting movements can be implemented at the same time and only with one machine element.
  • a large number of gears can be operated through the use of several partial gears and several clutch means if the switching device is characterized in that a stepper gear is arranged coaxially and laterally next to the shift shaft, the stepper gear being indirectly controlled by a superposition gear, the axis of rotation of the superposition gear is not arranged coaxially to the switching shaft.
  • the stepper gearbox then preferably actuates the pivotable supports directly or indirectly. Due to the non-coaxial arrangement of the superposition gear, the overall width remains narrow even when several partial gears are used.
  • the bottom bracket circuit with a switching device is particularly space-saving, characterized in that the second sun gear of the planetary gear is connected directly or indirectly to an actuator assembly.
  • Fig. 1 A side view of an electric bicycle with a bottom bracket shifter in a first embodiment.
  • FIG. 5 A cross section through the plane AB from Figure 4.
  • FIG. 6 A perspective view of the bottom bracket circuit from Figure 2 without the housing.
  • Fig. 13 A section through the stepper gear of the shift shaft of the bottom bracket gearshift.
  • the gear ratio which was selected by the user via a control element 11 on the handlebar 12, is regulated. Additional power is added to the pedaling power exerted by humans within the bottom bracket circuit 10. This additional power is provided by an electric motor.
  • the bottom bracket circuit 10 can be designed with or without an auxiliary drive.
  • the output shaft of the bottom bracket gearshift is coaxial with the bottom bracket shaft and carries the front pulley 8.
  • the front pulley 12 thus forms the transmission output. It rotates at different speeds relative to the crank arms 7, depending on which gear was engaged by the user of the vehicle.
  • the mechanical power is transmitted to the rear wheel 13 via a belt 12.
  • the front pulley 12 thus forms the transmission output.
  • the mechanical power is transmitted to the rear wheel via a belt 12.
  • the belt tensioner 20 is attached to the housing 22 of the bottom bracket circuit 10 via fastening plates 21.
  • the tension roller 23 is a component of the belt tensioner 20 and ensures correct belt tension in the belt 12, regardless of the position in which the rear wheel 13 is due to the suspension 16.
  • the bottom bracket circuit has a left protective cap 24, which protects the bottom bracket circuit from environmental influences. Another left protective cap 24 is located in front of the switching shaft, which is not visible here.
  • Figure 3 shows a side view of the bottom bracket circuit 10 from the right.
  • the illustration shows an example of an advantageous embodiment of the bottom bracket circuit with an integrated electric drive motor and electric switching actuation for bicycles with electric auxiliary drive.
  • the belt 12, the pedals 6 and the crank arms 7 are not shown in this illustration.
  • the bottom bracket circuit 10 in this embodiment can be dismantled into three assemblies, which are accommodated in a common multi-part housing and are described individually in more detail below.
  • the installation space of the respective assembly is outlined in dashed lines in Figure 3.
  • the manual transmission assembly 84 also contains the clutch and the connection to the actuating means as well as the new sensor arrangement with the electronic components that are responsible for determining the torque and the speed on the bottom bracket shaft 18.
  • a sensor 59 is arranged on the lateral surface of the input hollow shaft 60.
  • the cyclist's torque is thus directed from the pedals via the cranks 7 into the bottom bracket shaft 18 on both sides and then continued into the input hollow shaft 60.
  • a signal with information about the torque can be generated via the sensor 59, which rotates together with the input hollow shaft 60 during operation.
  • the sensor 59 which in an advantageous embodiment is designed as a strain gauge, not only the input hollow shaft 60 rotates, but also a rotating circuit board 44, which is able to further process the information about the torque.
  • the rotating circuit board 44 there are also sensors on the rotating circuit board 44 which are able to determine the position, orientation and speed of the input hollow shaft 60 in relation to the gear housing, to the stationary circuit board 45 and, if necessary, to the earth's magnetic field or gravity.
  • the signal transmission between the rotating and stationary circuit boards 44, 45 can take place wirelessly via radio, for example.
  • the energy that is required on the rotating circuit board 44 can be transmitted inductively from the circuit board 45 fixed to the housing. Other types of transmission are also possible.
  • the rotating circuit board 44 and the housing-fixed circuit board 45 are located centrally near the bottom bracket shaft 18 exactly between the first gear stage 74, which is located on the left in the direction of travel, and the second gear stage, which is located on the right in the direction of travel.
  • the novel bottom bracket circuit 10 has three drive gears 41, 42 and 43, which are coaxially firmly connected to the input hollow shaft 60.
  • the drive gear 41 has twenty teeth
  • the drive gear 42 has thirty-two teeth
  • the drive gear 43 has 53 teeth.
  • these gears are made in one piece and are connected in a twisted manner to the input hollow shaft 60 via a spline 73.
  • the idler gear with the smallest number of teeth is located at the outer end of the shift shaft 67 near the side wall of the left gear housing 35 and is connected to the largest drive gear. In this way, the shape of the switching shaft 67 can be chosen so that the deflection of the switching shaft 67 due to the radial gearing forces is minimized.
  • This idler gear with the smallest number of teeth has further properties: There is an optional needle bearing 27 between the idler gear 51 and the switching shaft 67. In addition, this idler gear with the smallest number of teeth has an internal toothing 57, which is axially spaced laterally from the running toothing.
  • the idler gears 51, 52, 53 can only transmit torque in one direction to the switching shaft 67.
  • the coupling means are constructed due to the shape of the internal toothing 57 and with the help of springs (not shown) in such a way that torques can only be positively transmitted in one direction.
  • the coupling body 58 slides on the internal teeth 57 and no torque can be transmitted.
  • the coupling means K1, K2 or K3 can assume an inactive state.
  • the table shows that the shift shaft 67 always rotates at least at the same speed as the bottom bracket shaft. This configuration is advantageous in that higher torques are never generated on the shift shaft 67 compared to the bottom bracket shaft. The torques on the switching shaft 67 are even much lower when the clutch means K3 or K2 are activated.
  • the novel switching shaft 67 shown has several non-coaxial bores in which there are several pivotable supports 61-66. The supports are cylindrical components that can pivot about their own axis and are led out of the switching shaft 67 at one axial end.
  • the actuating gear 68 is mounted on the reference gear 69 via a plain bearing 48 and secured axially outwards directly on the right side cover 81.
  • the actuating gear 68, the reference gear 69, the stepping gear 70 with the two associated internal teeth 71 and the six pivotable supports 61, 62, 63, 64, 65, 66 form part of the actuating means.
  • all six supports 61, 62, 63, 64, 65, 66 are pivoted and thus the coupling means K1, K2, K3, K4, K5 and K6 are actuated.
  • the idler gear 54 which has 20 teeth, is coupled to the switching shaft 67 via the activated clutch means K4.
  • the idler gear 55 which has 21 teeth, is coupled to the switching shaft via the activated clutch means K5.
  • the coupling means K6 couples the idler gear 56, which also has 21 teeth, to the switching shaft 67 in the same way.
  • the internal toothings 57 are geometrically the same in the first and second gear stages 74, 75, but are arranged in mirror images, since in the second gear stage 75 the torques have to be transmitted from the switching shaft 67 to the idler gears 54, 55 or 56.
  • the output hollow shaft 36 is arranged coaxially to the bottom bracket shaft 18 and, in an advantageous embodiment, is connected in one piece to three output gears.
  • the output gear 37 has 20 teeth, is arranged in the middle of the gear and meshes with the idler gear 54, which also has 20 teeth.
  • the output gear 38 has 32 teeth and meshes with the idler gear 55, which has 21 teeth.
  • the output gear 39 has 26 teeth and is located on the far right on the housing wall of the right gear housing 34. It meshes with the idler gear 56, which has 21 teeth.
  • the structure can be summarized as follows: It is a bottom bracket gear 10 with an actuating device, in particular for a vehicle powered by muscle power, with a first sub-gear 74 and a second sub-gear 75 which are connected in series for power transmission, the first Sub-transmission 74 and the second sub-transmission 75 have a switching shaft 67, on which a plurality of idler gears 51-56 are mounted, which form wheel pairs of the respective sub-transmission with a corresponding plurality of gears 37, 38, 39, 41, 42, 43, the Idler gears can be connected to the switching shaft 67 by means of pivoting coupling bodies 61-66.
  • the switching shaft 67 has a plurality of axial bores and the several axial bores of the switching shaft 67 are not coaxial with the switching shaft 67 are designed and there is a pivotable support 61-66 within the axial bores and in each case a pivotable support 61-66 is connected directly or indirectly to exactly one coupling body exclusively via its cylindrical lateral surface.
  • the following table shows the three possible gear ratios of the second gear stage 75 depending on the state of the clutch means K4, K5 and K6:
  • the output gears 37, 38 and 39 are connected to the side surfaces of the teeth via webs and are designed in one piece in such a way that excessive tooth root tensions can be prevented. Since the output hollow shaft 36 rotates at different speeds compared to the bottom bracket shaft 18, a double needle bearing 27 is provided. The bearing distance is specified via a spacer sleeve 26.
  • a driver 30 is attached to the hollow output shaft 36 using a spline 73 and secured axially using a shaft nut 29.
  • This structure also makes sense because the inner ring of the ball bearing 32” is also fixed in this way.
  • a shaft sealing ring 31 is arranged between the bottom bracket shaft 18 and the output hollow shaft 36.
  • the shaft seal ring 3T ensures a seal between the driver 30 and the right gear housing 34.
  • the driver 30 transmits the torque to the front pulley 8. Both components are screwed together.
  • This preferred new design of a bottom bracket shifter provides nine gears through the combination of the gear stages 74, 75. The following table shows the nine possible gear stages of the bottom bracket gear 10 depending on the state of all clutch means K1 to K6:
  • the exemplary design of the new product provides nine gears with even gradations, all of which are between 23.1 and 23.8%.
  • This gear gradation and the entire range of gear ratios of 538% is a very advantageous design, especially for bicycles with electrical assistance.
  • the innovation can be used in all e-bike categories, as the driving speed, which also depends on the diameter of the vehicle's driven wheel, can be adjusted using the so-called secondary gear ratio.
  • the secondary gear ratio is the ratio of the number of teeth on the front pulley 10 and the rear pulley, which is usually mounted on the rear wheel 13.
  • the novelty can not only be used on bicycles with electric assistance; this new bottom bracket circuit can also be used on vehicles without an auxiliary drive.
  • the bandwidth of 538% even allows use on a mountain bike. By eliminating individual pairs of gears, the new product can also be manufactured more cost-effectively and allows use in categories that require fewer gears and less bandwidth.
  • Figure 5 shows a cross section through the plane AB from Figure 4.
  • the bottom bracket shaft 18 rotates about the axis of rotation X1. Visible in this section is the shaft sealing ring 31, which prevents this Oil can escape from the left gearbox housing 35. Also visible is the largest drive gear 43, which has 53 teeth. As already explained before, this gear is used exclusively in gears seven, eight and nine for the three fastest or longest gear ratios. According to the advantageous design of the novelty, in order to save weight and installation space, the mechanical power of the auxiliary drive is also fed in via this gear 43.
  • at least one gear which is arranged coaxially to the bottom bracket shaft 18, is constantly connected to two other gears, one of the two gears being a step gear 98.
  • a step gear 98 consists of two gears that have a different number of teeth, are coaxially aligned with one another and are firmly connected to one another.
  • a step gear 98 is made in one piece.
  • the gear 87, which has 15 teeth, and the gear 88, which has 30 teeth, are designed in one piece as a step gear 98 and rotate about the rotation axis X7. X7 is therefore a rotation axis of the reducer.
  • This step gear 98 is mounted on an axle 99 fixed to the housing with the aid of a ball bearing 32′′.
  • the gear 92 is connected via a freewheel to the gear 90, which has 14 teeth and is designed in one piece as a shaft.
  • This freewheel 97 rotates around the rotation axis X5 and ensures that that the cyclist does not have to carry the electric motor along empty when the auxiliary drive is switched off or even operate it as a generator.
  • the gear 89 has 21 teeth, rotates about the rotation axis X6 and establishes a connection between the gear 90 and the gear 88.
  • the following table shows the gear ratios of the individual reduction stages and their rotation axes:
  • Figure 6 shows a perspective view of the bottom bracket circuit 10 from Figure 2. It shows the structure of the novel bottom bracket circuit 10 with an electric auxiliary drive in an advantageous embodiment. The electrical actuation is not visible in this view.
  • the left and right housing, the side covers, all screws, the pedal cranks 7, the front pulley 8, the plug contacts, the circuit board with the power electronics are not shown.
  • the advantageous embodiment is characterized in that the smallest idler gear 51 forms a pair of wheels with the largest drive gear 43 and is arranged laterally on the left in the direction of travel and that the largest drive gear 43 is also in a power-transmitting connection with another gear 87, this further gear 87 being in direct or indirect connection to the shaft 100 of the additional electric drive 102.
  • this additional gear 87 is located near or directly below the smallest idler gear 51. If you look at the cylindrical volume that encloses the largest drive gear 43, the left ball bearing of the bottom bracket shaft is also located in this volume.
  • the largest drive gear 43 has a bell-like shape and is materially connected to two further drive gears 41 and 42.
  • Each worm spring 106 is located in a groove 107, which is located on the lateral surface of the switching shaft 67.
  • the shift shaft 67 is also via a ball bearing 32 'in the right gearbox housing 34 stored.
  • This embodiment has the advantage that a rotation of, for example, 40 degrees on the actuating gear 68 causes a rotation of, for example, 120 degrees on the respective pivotable supports 61, 62, 63, 64, 65, 66.
  • the nine gear stages shown above are thus switched through with the help of a rotary movement of 8 times 40 degrees on the actuating gear 68. This corresponds to a rotation of 320 degrees.
  • the useful new gear ratios listed above can be easily implemented within the scope of the embodiment shown if the gear unit is characterized in that the root diameter of the external toothing of the idler gear 51, which has an internal toothing 57 that is laterally spaced, is characterized in that the root diameter is smaller or is equal to the maximum diameter of the internal teeth.
  • this design can even be improved in terms of strength if the novelty is characterized in that at least this one idler gear 51, which has internal teeth that are laterally spaced, is characterized in that the teeth of the external teeth, which represent the running teeth , are materially connected to each other laterally. In parallel, there is also further reinforcement if at least the idler gear 51, which has an internal toothing 57 that is laterally spaced, is characterized in that the teeth of the internal toothing 57 are materially connected to one another laterally. It is clear from the illustration that the switching shaft 67 in the area in which it is connected to the idler gear 51, which has internal teeth 57 that are laterally spaced, is characterized by the fact that the switching shaft 67 has two different outer diameters in this area owns.
  • Figure 8a shows the clutch body 58 completely submerged within the pocket, which is milled as a recess on the lateral surface of the switching shaft 67.
  • the coupling body 58 is not connected to the internal toothing 57 of the idler gear 56.
  • the idler gear 56 can rotate freely in both directions of rotation.
  • the coupling means is deactivated in both directions of rotation.
  • the pivoting support 66 is not in direct contact with the coupling body.
  • Figure 8b shows the clutch body 58 completely coupled into the internal teeth 57 of the ring gear.
  • the coupling agent is activated.
  • the cylindrical lateral surface of the pivotable support 66 is in a force-transmitting connection with the clutch body 58. In this state, the switching shaft can transmit a torque to the idler gear 56 in a clockwise direction.
  • Figure 8c shows the state when the idler gear 56 rotates clockwise faster than the switching shaft 67 when the clutch means is activated. In this state, the back of the clutch body 58 slides over the internal teeth 57. This state can occur briefly during the switching process.
  • Figure 9a, Figure 9b and Figure 9c show the detail A1 from the sectional view of Figure 8 in a schematic representation in general for such a coupling means K according to the novelty.
  • the switching shaft 67 rotates about the rotation axis X2.
  • the idler gear 109 rotates counterclockwise and drives the switching shaft 67.
  • the internal toothing 57 is located concentrically in the idler gear 109. It has bearing surfaces 112, pressure surfaces 110 and sliding surfaces 111.
  • the pivotable support 114 can assume a second state in which the pivotable support 114 is not connected to the coupling body 114 is connected. In this second state, this clutch body 114 cannot be brought into a force-transmitting connection to the idler gear 109 and, regardless of the direction of rotation of the idler gear 109, no surface of the internal toothing 57 can come into connection with the clutch body 58.
  • the idler gear 109 can slide on the switching shaft 67 without making any noise.
  • the coupling means is shown deactivated in Figure 9c. 9 also shows that the recess 107, in which a coupling body 58 is located, is connected to the bore 113 via an opening 119, in each of which there is a pivotable support 114.
  • This type of arrangement is of course also able to transfer the forces in reverse from the clutch body to the idler gear 109.
  • the following description selects the case in which the forces from the idler gear 109 are transmitted to the clutch body 58 on the clutch body 58.
  • the clutch body 58 is located on the switching shaft 67 within a pocket 107, which can also be described as a recess within the lateral surface of the switching shaft 67.
  • the clutch body 58 is mounted on surface 137 on the switching shaft 67 and can therefore rotate about the rotation axis X8.
  • the force Fk 124 which is applied to the clutch body 58 by the idler gear 109, is derived from the support force Fa 140 into the switching shaft 67.

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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)
  • Gear-Shifting Mechanisms (AREA)
  • Structure Of Transmissions (AREA)

Abstract

L'invention se rapporte à un dispositif de changement de vitesse de jeu de pédalier (10) avec un dispositif de changement de vitesse (188), en particulier pour un véhicule à propulsion musculaire, comprenant un mécanisme d'engrenage qui présente un arbre de sélecteur (67) sur lequel une pluralité de roues folles (109) sont montées, lesdites roues folles formant des paires de roues conjointement avec une pluralité correspondante de roues d'engrenage, les roues folles (109) pouvant être reliées à l'arbre de sélecteur (67) au moyen de corps d'accouplement (58). Le dispositif de changement de vitesse de jeu de pédalier (10) est caractérisé en ce que l'arbre de sélecteur (67) présente deux ou plus de deux chambres (143) qui sont agencées parallèlement ou virtuellement parallèlement à un axe de l'arbre de sélecteur (67), et les deux ou plus de deux chambres (143) de l'arbre de sélecteur (67) sont conçues pour ne pas être coaxiales à l'axe de l'arbre de sélecteur (67). De plus, un support pivotant respectif (114) est situé à l'intérieur d'au moins deux chambres (143). Un support pivotant (114) peut adopter un premier état dans lequel le support pivotant (114) est directement ou indirectement relié à précisément un corps d'accouplement (58), et dans le premier état, le corps d'accouplement (58) peut être amené dans une liaison de transmission de force avec une roue folle (109). De plus, la surface latérale de l'arbre de sélecteur (67) présente des dépressions (107) dans lesquelles sont situés des corps d'accouplement (58), et au moins deux dépressions (107) sont reliées à au moins une chambre (143) par l'intermédiaire d'une ouverture respective (119).
PCT/EP2023/051076 2022-05-17 2023-01-18 Dispositif de changement de vitesse de jeu de pédalier avec dispositif de changement de vitesse pour une bicyclette, et bicyclette comprenant un tel dispositif de changement de vitesse de jeu de pédalier WO2023222260A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102022001739.3A DE102022001739A1 (de) 2022-05-17 2022-05-17 Tretlagerschaltung mit Schaltvorrichtung für ein Fahrrad und ein Fahrrad mit einer solchen Tretlagerschaltung
DE102022001739.3 2022-05-17

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DE19750659A1 (de) 1997-11-15 1999-05-20 Schmidt Christa Zweiradfahrzeug, insbesondere Fahrrad
US5924950A (en) 1997-10-06 1999-07-20 Pusic; Pavo M Even increment, non-overlapping bicycle transmission
FR2776613A1 (fr) 1998-03-25 1999-10-01 Pierre Louis Marie Portalier Boite de vitesses a 8 ou 12 rapports regulierement etages et commandes par une seule manette, a installer sur une bicyclette ordinaire
EP1445088A2 (fr) 2001-08-22 2004-08-11 José Miguel Llibrer Porcar Systeme de changement de vitesse mecanique pour bicyclettes et vehicules analogues
EP1982913A1 (fr) 2006-02-10 2008-10-22 Fujiwara Wheel Incorporated Transmission pour bicyclette
WO2009132605A1 (fr) 2008-04-30 2009-11-05 Karlheinz Nicolai Transmission à engrenages multiples à commande magnétique
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DE102011106107A1 (de) * 2011-06-09 2012-12-13 Pinion Gmbh Schaltvorrichtung und Getriebeeinheit
EP2379402B2 (fr) 2008-12-22 2017-08-23 Pinion GmbH Ensemble transmission
US10526044B2 (en) 2014-04-14 2020-01-07 Pinion Gmbh Shifting device and shifting pawl for a shifting device
DE102009060484B4 (de) 2009-12-18 2020-04-16 Pinion Gmbh Mit Muskelkraft antreibbares Fahrzeug
US20210172502A1 (en) * 2018-07-10 2021-06-10 Eun Su Han Multi-speed transmission
DE102013112788B4 (de) 2013-11-19 2021-12-16 Pinion Gmbh Schaltvorrichtung und Getriebeeinheit

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KR101249813B1 (ko) 2012-08-31 2013-04-02 한은수 기어 이동 어셈블리 및 그를 구비하는 변속기
KR101782895B1 (ko) 2016-05-12 2017-09-28 복 성 김 자전거 변속허브
DE102017008376B9 (de) 2016-12-06 2018-06-21 Jürgen Karrenberg Mehrstufiges Lastschaltgetriebe, vorzugsweise für Fahrzeuge mit Fußschaltung
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Publication number Priority date Publication date Assignee Title
DE967668C (de) 1952-04-10 1957-12-05 Nsu Werke Ag Getriebeanordnung
DE1113618B (de) 1957-01-11 1961-09-07 Siemens Ag Schrittschaltgetriebe
DE19720794A1 (de) 1997-05-16 1998-11-19 Bernhard Rohloff Mehrgang-Getriebenabe
US5924950A (en) 1997-10-06 1999-07-20 Pusic; Pavo M Even increment, non-overlapping bicycle transmission
DE19750659A1 (de) 1997-11-15 1999-05-20 Schmidt Christa Zweiradfahrzeug, insbesondere Fahrrad
FR2776613A1 (fr) 1998-03-25 1999-10-01 Pierre Louis Marie Portalier Boite de vitesses a 8 ou 12 rapports regulierement etages et commandes par une seule manette, a installer sur une bicyclette ordinaire
EP1445088A2 (fr) 2001-08-22 2004-08-11 José Miguel Llibrer Porcar Systeme de changement de vitesse mecanique pour bicyclettes et vehicules analogues
EP1982913A1 (fr) 2006-02-10 2008-10-22 Fujiwara Wheel Incorporated Transmission pour bicyclette
US20110120794A1 (en) 2008-02-04 2011-05-26 Clean Mobile Ag Chain Gear, Vehicle Comprising a Chain Gear and Method for Transforming a motor Torque in a Vehicle
WO2009132605A1 (fr) 2008-04-30 2009-11-05 Karlheinz Nicolai Transmission à engrenages multiples à commande magnétique
EP2379402B2 (fr) 2008-12-22 2017-08-23 Pinion GmbH Ensemble transmission
WO2010134732A2 (fr) * 2009-05-19 2010-11-25 Hyun Kyung Yul Transmission automatique multirapport
DE102009060484B4 (de) 2009-12-18 2020-04-16 Pinion Gmbh Mit Muskelkraft antreibbares Fahrzeug
DE102011106107A1 (de) * 2011-06-09 2012-12-13 Pinion Gmbh Schaltvorrichtung und Getriebeeinheit
DE102013112788B4 (de) 2013-11-19 2021-12-16 Pinion Gmbh Schaltvorrichtung und Getriebeeinheit
US10526044B2 (en) 2014-04-14 2020-01-07 Pinion Gmbh Shifting device and shifting pawl for a shifting device
US20210172502A1 (en) * 2018-07-10 2021-06-10 Eun Su Han Multi-speed transmission

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DE102022001739A1 (de) 2023-11-23

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