WO2021156149A1 - Transmission et entraînement auxiliaire pour une bicyclette - Google Patents

Transmission et entraînement auxiliaire pour une bicyclette Download PDF

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Publication number
WO2021156149A1
WO2021156149A1 PCT/EP2021/052141 EP2021052141W WO2021156149A1 WO 2021156149 A1 WO2021156149 A1 WO 2021156149A1 EP 2021052141 W EP2021052141 W EP 2021052141W WO 2021156149 A1 WO2021156149 A1 WO 2021156149A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
wobble
shaft
drive
output shaft
Prior art date
Application number
PCT/EP2021/052141
Other languages
German (de)
English (en)
Inventor
Wolfgang Rodi
Albert Schlumberger
Original Assignee
Rolless Gmbh
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 Rolless Gmbh filed Critical Rolless Gmbh
Publication of WO2021156149A1 publication Critical patent/WO2021156149A1/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
    • 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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • F16H1/321—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear the orbital gear being nutating

Definitions

  • the present invention relates to a transmission and an auxiliary drive for a vehicle, in particular a bicycle.
  • an auxiliary drive for a bicycle in which the essential components are arranged coaxially.
  • the pin ring gear used here comprises an outer ring with internal teeth and a flexible pin ring which is mounted on the outer circumference of an elliptical rotating body. By turning the elliptical rotating body within the pin ring, the pin ring is deformed and brought into engagement in sections with the internal teeth of the outer ring.
  • the transmission has a relatively good efficiency and can withstand high torques, al ler however the auxiliary drive for a bicycle equipped with it is relatively large, wide and heavy in diameter.
  • DE 2 162 867 A discloses a so-called swash plate transmission, in which the essential components for power transmission are also arranged along an axis.
  • a transmission has a fixed bevel gear and a wobble gear, which is also designed as a bevel gear and meshes with the fixed bevel gear wheel.
  • the wobble gear is rotatably mounted on a stub shaft, which is formed eccentrically on a drive shaft in such a way that its axis and thus the bevel axis of the wobble gear is aligned obliquely to the axis of the drive shaft.
  • swash plate gears are generally sliding wedge gears in which, due to the sliding movement between the tooth flanks, a sliding friction arises during torque transmission, which results in a relatively poor degree of efficiency.
  • transmission of the torque from the wobble gear to the output shaft with as little loss as possible and a compact mounting of the wobble gear are difficult to implement with limited installation space.
  • DE 11 2016 002 380 T5 describes a wobble plate gearbox in which the efficiency is to be improved by a further wobble gear and a specific toothing geometry.
  • auxiliary drive for a vehicle uses a Tau mel transmission to enable a space-saving structure.
  • the auxiliary drive can also be used as a generator.
  • the electric motor must also be turned, which causes a higher resistance and can have a negative effect on the driving experience.
  • the present invention is therefore based on the object of providing a transmission or an auxiliary drive for a vehicle, in particular a bicycle, which are as small and light as possible and at the same time provide the necessary reduction and a good degree of efficiency.
  • a swash plate transmission for a vehicle in particular a bicycle, comprises a drive shaft which is designed as a hollow shaft and can be driven by a power source, in particular an electric motor; an output shaft which is designed as a hollow shaft and defines a transmission axis to which the drive shaft is coaxially angeord net; a first bevel gear which is arranged coaxially with the transmission axis; and a first wobble gear, which is designed as a bevel gear with a first bevel axis and meshes with the first bevel gear.
  • the first wobble gear is mounted on the drive shaft in such a way that the first conical axis of the first wobble gear is arranged at an angle to the gearbox and intersects it. At least one of the first bevel gear and the first wobble gear is set up to revolve in order to transmit a rotary movement to the output shaft.
  • the first wobble gear has a wobble angle which is between +/- 1 ° and +/- 10 °.
  • the first bevel gear and / or the first wobble gear preferably have a gear cone angle which is between 20 ° and 40 °.
  • a swash plate transmission is provided for a vehicle, which can be designed in a particularly space-saving and easy manner, in particular as a bottom bracket transmission of a bicycle, and can be easily integrated into a bicycle frame.
  • the swash plate gear is used to convert torque between the drive shaft and the output shaft.
  • the wobble gear is rotatably Gela Gert relative to the drive shaft. Because the first conical axis of the first wobble gear is arranged at an angle to the transmission axis and intersects this, a wobble movement of the first wobble gear occurs during one rotation of the drive shaft, which has a movement component in the axial direction of the transmission axis and a movement component in the direction of rotation of the drive shaft. In the circumferential direction, a ring gear portion of the first wobble gear is therefore continuously moved into engagement with the first bevel gear, while already engaged portions of the ring gear of the first wobble gear are moved away from the first bevel gear and thus out of engagement.
  • the output shaft has an axis of rotation which is intended to define the transmission axis here. It goes without saying that, as an alternative, another axis can also be viewed as the reference axis.
  • the intersection between the first cone axis of the first wobble gear and the Ke gel axis of the first bevel gear, which is coaxial with the transmission axis, is stationary. This point of intersection is also known as the wobble point.
  • the wobble point is defined as the pivot point of the respective wobble gear and lies on the transmission axis.
  • the wobble point is arranged to be stationary.
  • the angle between the first cone axis and the transmission axis corresponds to the tumble angle by which the first wobble gear moves to and from the first bevel gear.
  • the wobble angle is defined between an axis that is aligned perpendicular to the gear axis at the wobble point and a maximum deflection of the respective wobble gear in the direction of the drive (positive sign) or in the direction of the output (negative sign).
  • the wobble angle can be specified as the angle between the cone axis of the respective wobble gear and the gear axis and have a positive or negative sign. Since the wobble angle in the direction of the drive is the same as the wobble angle in the direction of the output, the wobble angle is given here with both signs (+/-).
  • the wobble angle of a wobble gear is therefore e.g. +/- 10 ° or +/- 5 °.
  • swash plate gears are sliding wedge gears in which the tooth flanks of a wobble gear and a corresponding bevel gear slide along one another while they are in engagement.
  • the resulting sliding friction has a negative effect on the efficiency of the transmission. It has been found that with high performance, for example in the nominal range of electrical auxiliary drives for bicycles, even small Gleitbewe movement between the wobble gear and the bevel gear are sufficient to cause high efficiency losses and strong heating of the transmission.
  • the wobble angle is between +/- 1 ° and +/- 10 °, such sliding movement and thus the friction and efficiency losses can be minimized. be mized, while with increasing wobble angles the sliding movement and loss power increases.
  • a small wobble angle also has the advantage that the oscillation amplitude of the respective wobble gear is small and the reaction forces on the housing or on the bicycle can be reduced as a result.
  • the surface pressure on the individual teeth or their tooth flanks can be reduced and the fatigue strength of the gear can be increased.
  • the distance between adjacent tooth flanks of the wobble gear and the bevel gear can be minimized when the teeth are immersed or engaged, so that under load a small elastic deformation is sufficient to bring more teeth into mesh at the same time. This enables high torques to be transmitted even in a small installation space.
  • the first bevel gear or the first wobble gear does not rotate around the transmission axis.
  • the rotating first wobble gear has 50 teeth and the stationary bevel gear mounted centrally to the drive shaft has 49 teeth.
  • the respective number of teeth can be multiplied, e.g. doubled (100: 98), tripled (150: 147) or quadrupled (200: 196) etc.
  • the multiplication of the respective number of teeth has the advantage that more teeth are in contact with the load and thus the load or surface pressure on each meshing tooth is reduced.
  • the first bevel gear and the first wobble gear preferably have a number of teeth which is between 20 and 80, preferably between 30 and 60, more preferably between 35 and 50. It is also conceivable that the first bevel gear and the first wobble gear each have a multiple of this number of teeth, in particular double or three times as many teeth with a constant reduction. While the vibrations or accelerations of the first wobble gear and the associated frictional losses increase disproportionately with an increasing reduction, the weight and size of the drive motor decreases, as the drive speed increases or the drive torque decreases.
  • the swash plate transmission therefore preferably brings about a reduction between 20 and 80, preferably between 30 and 60, more preferably between 35 and 50, in order to be particularly suitable for use in the field of bicycles, in particular pedelecs or e-bikes.
  • the first bevel gear and the first wobble gear are preferably each mounted outside the drive or output shaft.
  • the first bevel gear can be mounted radially outside the input shaft and the output shaft in a housing of the transmission.
  • the first bevel gear can also be mounted directly or indirectly on the output shaft or be formed integrally with the output shaft. It then extends from the output shaft radially outward.
  • the drive shaft has a shaft section which forms a bearing seat for mounting the first Tau melyakrads.
  • This shaft section has a cylindrical outer surface, the axis of which is oriented obliquely to the gear axis or to the longitudinal axis of the drive shaft and intersects this.
  • a conventional roller bearing is preferably arranged on the cylindrical outer surface or the bearing seat formed by it, e.g. B. a ball bearing.
  • a plurality of roller bearings can also be provided.
  • the first wobble gear is mounted on the roller bearing so that it can be rotated relative to the drive shaft.
  • a first hollow shaft is mounted on the outer ring of the roller bearing and the first wobble gear is fixedly connected to the first hollow shaft or formed integrally.
  • Alternative designs and bearings for the first wobble gear are conceivable.
  • the wobble plate transmission in one embodiment comprises a compensating device which is set up to compensate for an axial movement component of the wobble movement of the first wobble gear with respect to the transmission.
  • the compensation device preferably comprises an axially fixed component and an axially movable component connected to the wobble gear.
  • the axially fixed component and the axially movable component are connected to one another in such a way that they can be moved relative to one another in the axial direction.
  • the axially fixed component and the axially movable component are preferably essentially not movable relative to one another in the circumferential direction. They are then connected to one another in a rotationally fixed manner.
  • the axially movable component of the compensating device is preferably connected in a rotationally fixed manner to the first wobble gear.
  • the compensation device is preferably arranged in the direction of the transmission axis at the level of the Tau melyaks. Loads are then evenly distributed. In addition, the slightest movement takes place at this point, so that only slight accelerations act on the components of the compensation device.
  • the compensation device is designed as a ball joint in a preferred embodiment.
  • the ball joint can have an outer shell or an outer ring and an inner shell or an inner ring.
  • a plurality of balls are received between the outer ring and the inner ring.
  • grooves facing one another are formed in both the inner ring and the outer ring.
  • the grooves extend in the axial direction of the respective ring.
  • One groove in each case in the inner ring is aligned with a groove in the outer ring in order to jointly form an axial guide for receiving a ball.
  • the grooves have a length in the axial direction that is greater than the diameter of the balls in order to allow relative movement between the inner ring and the outer ring in the axial direction.
  • the width of the grooves in the transverse direction i.e. essentially in the circumferential direction of the inner and outer rings, is preferably adapted to the diameter of the balls, so that a relative movement between the inner ring and the outer ring in the circumferential direction of the rings is essentially not possible.
  • the drive shaft and the drive shaft from are arranged side by side in the axial direction.
  • the side of the transmission in which the drive shaft is arranged is therefore also described as the drive side or "drive side”.
  • the side of the gearbox in which the output shaft is arranged is therefore also described as the output side or "output side”.
  • the drive side and the output side write two axially opposite sides of the transmission.
  • the first bevel gear is fixedly mounted in a housing of the swash plate gear.
  • the first bevel gear is consequently fixed on the housing both in the axial direction and in the circumferential direction.
  • the first bevel gear is preferably arranged on the drive side of the first wobble gear.
  • a compensation device is preferably arranged between the first wobble gear and the output shaft.
  • the compensating device is preferably arranged on the output side of the first wobble gear.
  • a movement of the first wobble gear in the circumferential direction is transmitted via the compensation device to a hollow shaft, which is preferably formed by the output shaft of the wobble plate transmission.
  • the first wobble gear is attached to a drive-side end of a first hollow shaft or is formed integrally therewith.
  • the output-side end of the first hollow shaft forms the axially movable component of the compensation device, in particular one of the inner ring and outer ring of a corresponding Ku gel joint.
  • the axially fixed component of the compensating device for example formed by the other of the inner ring and outer ring of the corresponding Ku gel joint, is non-rotatably connected to the output shaft of the swash plate gear and can, for example, be formed integrally with it.
  • the first bevel gear is firmly connected to the output shaft.
  • the first bevel gear can be mounted on the output shaft, fixedly attached to the output shaft, or formed integrally with the output shaft.
  • the first bevel gear is preferably fixed both in the axial direction and in the circumferential direction with respect to the output shaft.
  • the first bevel gear is consequently arranged on the output side of the first wobble gear.
  • a compensation device is preferably arranged between the first wobble gear and a housing of the transmission. Due to the arrangement of the first wobble gear and the first bevel gear, the compensation device is preferably arranged on the drive side of the first wobble gear.
  • the axially fixed existing component of the compensation device for. B. the outer ring of a ball joint can be fixed on the housing of the transmission, while the axially movable component te of the compensation device, then z. B. the inner ring of the ball joint is firmly connected to the first wobble gear.
  • Both the axially movable component and the first wobble gear are preferably formed integrally with a first hollow shaft and arranged opposite one another at one end of the first hollow shaft.
  • the swash plate transmission has two gear wheel pairs, that is to say further comprises a second bevel gear and a second swash gear.
  • the second bevel gear is net angeord coaxially to the transmission axis.
  • the second wobble gear is designed as a bevel gear with a second bevel axis, meshes with the second bevel gear and is mounted on the drive shaft in such a way that the second bevel axis of the second wobble gear is arranged at an angle to the transmission axis and intersects it.
  • the first and the second wobble gear are preferably firmly connected to one another, that is to say fixed relative to one another both in the circumferential direction and in the axial direction of the first and the second cone axis.
  • the first and second wobble gears can also be integrally formed.
  • the first and second wobble gears are arranged koaxi al. The first and the second cone axis thus coincide.
  • the first bevel gear is vorzugswei se analogously to the second embodiment firmly connected to the output shaft, supported on this or formed integrally with it.
  • the second bevel gear is preferably firmly connected to the housing and fixed on the housing both in the circumferential direction and in the axial direction of the second cone axis.
  • the second bevel gear can be arranged on the drive side or on the output side of the second wobble gear.
  • this comprises, as described above, two gear wheel pairs and the first and the second swash gear wheel are oriented in the same direction.
  • the first and second wobble gears preferably point in the direction of the output and the first and second bevel gears are arranged on the output side of the two wobble gears.
  • the first and second wobble gears are firmly connected to one another, in particular fixed to one another both in the axial direction and in the circumferential direction.
  • one of the two wobble gears is formed integrally with a first hollow shaft and the other wobble gear is fixedly attached to the first hollow shaft.
  • the first and second wobble gears can also be formed separately and connected to one another or to the first hollow shaft. This facilitates the manufacture of the wobble gears, in particular the teeth of the same.
  • the first and the second wobble gear can be formed integrally with one another or with the first hollow shaft.
  • the swash plate transmission also comprises two gear wheel pairs, that is to say a first and a second bevel gear and a first and a second wobble gear, the first and second wobble gears being fixedly connected to each other and oriented in opposite directions.
  • the first wobble gear is preferably oriented in the direction of the output and the second wobble gear in the direction of the drive.
  • the first bevel gear is then arranged on the output side and the second bevel gear on the drive side of the two wobble gears.
  • first wobble gear and the second wobble gear are formed integrally with a first hollow shaft, one of the two wobble gears being arranged at each end of the first hollow shaft. Furthermore, the first wobble gear and the second wobble gear are diagonally relative to one another in mesh with the respective bevel gear.
  • the swash plate transmission can furthermore have a balancing mass for balancing out vibrations induced by the wobbling movement of the first wobble gear and, if provided, the second wobble gear.
  • vibrations are induced by the shift in the center of gravity when the wobble gear or gears revolve around the transmission axis. These vibrations can be taken into account in the design and arrangement of the balancing weight, or at least one additional balancing weight can be provided to compensate for these vibrations.
  • the balancing mass is provided on the drive shaft on which the Tau melyakrad is mounted.
  • All balancing masses described herein can be designed as separate elements and attached to the water radially inside or radially outside of the drive shaft.
  • weights can be used for this purpose, which are arranged according to the imbalance along the circumference of the drive shaft.
  • the balancing mass can, however, also be formed integrally with the drive shaft.
  • the drive shaft can have a reinforced cross-section in sections, which is formed, for example, by a section-wise greater or lesser wall thickness of the drive shaft formed as a hollow shaft.
  • the drive shaft can have at least one, preferably a plurality of bores in its lateral surface. This enables local mass differences to be set precisely.
  • a plurality of bores is provided, which can be designed as through bores. The plurality of bores are arranged in the axial direction and in the circumferential direction ver sets to each other.
  • a plurality of balancing masses is provided accordingly to the balancing mass described above, whereby a very flexible and optimized compensation of vibrations can take place.
  • the plurality of balancing masses preferably comprises at least a first and a second balancing mass corresponding to the balancing mass described above.
  • the plurality of compensation masses are arranged at a distance from one another in the axial direction of the drive shaft and preferably also in the circumferential direction.
  • the mass of the plurality of balancing masses can differ.
  • the first wobble gear and, if provided, also the second wobble gear preferably has the shape of a hollow bevel gear with internal teeth.
  • the respective wobble gear then has at least one more tooth than the associated bevel gear.
  • the wobble gear could also be designed as a bevel gear with external teeth, but would then have to have at least one tooth less than the associated bevel gear. Such an embodiment leads to a more complex and difficult to manufacture transmission and is therefore not tert erläu detail.
  • the first bevel gear and / or the first wobble gear preferably have a gear cone angle which is between 25 ° and 35 °.
  • the gear cone angle of the first wobble gear and the first bevel gear is preferably equal.
  • the swash plate gear also comprises a second bevel gear and a second wobble gear
  • these preferably have a gear cone angle that is between 10 ° and 60 °, preferably between 15 ° and 40 °, more preferably between 20 ° and 35 ° ° is.
  • the gear cone angle of the second wobble gear and the second bevel gear is preferably the same.
  • the gear cone angles of the first and second wobble gears preferably differ.
  • one of the two wobble gears has a toothed wheel cone angle which is between 10 ° and 60 °, preferably between 20 ° and 50 °, more preferably between 25 ° and 40 °
  • the other wobble gear has a gear wheel cone angle which is between 5 ° and 30 °, preferably between 10 ° and 25 °, more preferably given between 12 ° and 20 °.
  • the gear cone angle is defined herein as the angle between an axis that is perpendicular to the cone axis of the respective (wobble or bevel gear) and a surface line of the respective (wobble or bevel) gear, which passes through the tips of the respective Teeth is formed.
  • the first wobble gear preferably has a wobble angle between +/- 1 ° and +/- 6 °, preferably between +/- 1.5 ° and +/- 4 °, preferably between 12 and +/- 3.5 ° is.
  • this also preferably has a wobble angle that is between +/- 1 ° and +/- 10 °, preferably between +/- 1 ° and +/- 6 °, more preferably between +/- 1, 5 ° and +/- 4 °, and even more preferably between +/- 2 ° and +/- 3.5 °.
  • the definition of the wobble angle applies analogously to the first and second wobble gear.
  • the wobble point is also defined here as the pivot point of the second wobble gear and lies on the transmission axis. More precisely, the wobble point is at the intersection between the cone axis of the second wobble gear and the transmission axis.
  • a tooth tip of a wobble gear follows a curve which, in the case of a gear, leads to a cone angle of 0 ° to about 15 ° to a considerable sliding movement between the tooth flanks.
  • the following dependency preferably arises between the gear ratio and the gear cone angle: If the gear cone angle of the wobble gear or the bevel gear (on the ordinate) is plotted against the gear ratio (on the abscissa), a function is created that essentially defines the shape a hyperbola. An optimal gear cone angle can then be determined as a function of the desired gear ratio.
  • the gear cone angle is preferably selected from a range of +/- 5 ° around the value of the gear cone angle determined in this way.
  • the tooth flanks of the first bevel gear and / or the first wobble gear and, if present, the second bevel gear and / or the second wobble gear are preferably essentially straight. As a result, the gears can be manufactured particularly easily and inexpensively.
  • both the tooth flanks of the first bevel gear and those of the first wobble gear are straight and, if present, both the tooth flanks of the second bevel gear and the second wobble gear are straight.
  • the gear can then be designed in such a way that the tooth flanks touch you flat when the teeth are rolling. As a result, a relatively low surface pressure in the area of the tooth flanks is sufficient and the load and wear of the teeth are minimized.
  • the tooth flanks of the first bevel gear and / or of the first wobble gear preferably have a flank angle between 10 ° and 50 °, preferably between 20 ° and 40 °, preferably between 25 ° and 35 °.
  • the tooth flanks of the second bevel gear and / or of the second wobble gear preferably have a flank angle between 10 ° and 70 °, preferably between 20 ° and 60 °.
  • the flank angle of the tooth flanks of a wobble gear differs from the flank angle of the tooth flanks of the associated bevel gear.
  • the difference between the flank angle of the tooth flanks of the wobble gear and the flank angle of the tooth flanks of the bevel gear is preferably between 0.5 ° and 5 °.
  • the flank angle is defined between the respective tooth flank and a central or symmetry plane of the two tooth flanks of a tooth.
  • a small flank angle corresponds to a steep tooth flank.
  • a small flank angle leads to larger contact surfaces of the meshing teeth and thus to lower surface pressures.
  • a smaller flank angle results in lower axial forces, which means that lower loads are exerted on the bearings of the gearbox and bearing friction and wear can be reduced.
  • high axial forces push the wobble gear and the bevel gear apart, so that the sliding movement can be amplified, which in turn can be avoided by using small flank angles.
  • a transmission according to the invention is particularly preferably used in a drive for a vehicle, in particular a bicycle.
  • a drive according to the invention for a vehicle, in particular a bicycle comprises a motor with a shaft driven by the latter; an output shaft for driving the vehicle; and a swash plate transmission according to one of the embodiments described above, which is vorgese hen between the driven shaft and the output shaft for torque conversion between the driven shaft and the output shaft.
  • the drive shaft of the swash plate gear is formed integrally with the shaft driven by the motor or coupled to the shaft driven by the motor, preferably connected in a rotationally fixed manner.
  • the output shaft of the swash plate gear is coupled to the output shaft, preferably connected in a rotationally fixed manner at least in the drive direction.
  • a drive for a vehicle in particular a bicycle, an e-bike or a pedelec, is provided which is very simple and space-saving and has a low weight.
  • the output shaft is mounted radially outward on the housing of the swashplate drive or supported on this and mounted radially inward on the output shaft or supported on this.
  • a particularly space-saving structure in particular in the axial direction, can be achieved.
  • a particularly good mounting is sufficient if the output shaft is mounted on the output shaft by means of a first and a second roller bearing and is mounted on the housing by means of a third roller bearing. Large forces can be supported on the housing via the third roller bearing, which at the same time enables a construction that is as space-saving as possible.
  • the output shaft is preferably designed as a hollow shaft.
  • the motor is preferably an electric motor, which can be designed as an external rotor or an internal rotor.
  • the electric motor includes a rotor and a stator.
  • the rotor and the stator are preferably arranged coaxially to the transmission axis.
  • the drive preferably further comprises an energy source, in particular in the form of a rechargeable battery, which is electrically connected to the motor.
  • the connection between the motor and the energy source can be made separable so that the energy source z. B. can be removed from the rest of the drive for charging and storage.
  • the drive preferably provides a torque between 40 and 150 Nm, preferably between 100 and 140 Nm, more preferably between 120 and 130 Nm on the output shaft.
  • the peak power of the drive is preferably up to 1000 watts.
  • the nominal power for an e-bike or pedelec is preferably 250 watts and for a speed or S-pedelec 500 watts.
  • the wobble plate transmission described at the beginning can ensure that the overall drive (motor and wobble plate transmission) has an efficiency of over 80%.
  • the drive further comprises a bottom bracket shaft which is arranged coaxially to the transmission axis and extends through the drive shaft and the drive shaft.
  • a crank with a pedal is preferably attached to both ends of the bottom bracket shaft in order to manually set the bottom bracket shaft in rotary motion and thus enable manual drive.
  • the lateral distance in the axial direction of the bottom bracket shaft between the mounting points of the pedals on the crankset is defined as the Q factor and is preferably less than or equal to 176 mm.
  • the drive is set up to transmit a torque introduced manually via the bottom bracket shaft to the output shaft.
  • the bottom bracket shaft is preferably coupled to the output shaft in a rotationally fixed manner at least in the drive direction of the output shaft.
  • the output shaft is designed as a hollow shaft and rotatably mounted relative to the bottom bracket shaft on the T retlagerwelle and / or in a housing of the drive.
  • the drive preferably comprises a first freewheel and a second freewheel.
  • a freewheel enables power to be transmitted between two shafts in one direction of rotation, e.g. B. in the drive direction of the output shaft, and prevents power transmission in the other direction of rotation.
  • the first freewheel is arranged between the output shaft of the swash plate gear and the output shaft and couples them with one another in such a way that a rotary movement is transmitted from the output shaft to the output shaft in only one direction of rotation or circumferential direction.
  • the first freewheel is preferably arranged in the axial direction of the output shaft between tween the first and the second roller bearing, by means of which the output shaft is mounted on the output shaft.
  • the second freewheel is arranged between the bottom bracket shaft and the output shaft and couples them to one another in such a way that a rotary movement is transmitted from the bottom bracket shaft to the output shaft in only one direction of rotation or circumferential direction.
  • the first and the second freewheel can be designed independently of each other as a Klemmkör pergollauf, as a pawl freewheel or as a ratchet freewheel (DT Swiss Ratchet).
  • the motor is designed as an electric motor and the motor and the output shaft are arranged coaxially to the transmission axis.
  • all essential components of the drive in particular the drive shaft, the Abreteswel le, the bottom bracket shaft, the output shaft and the electric motor are arranged coaxially to the transmission axis. This enables a particularly space-saving structure.
  • the drive shaft of the swash plate gear can also be formed integrally with a driven hollow shaft of the electric motor.
  • the energy source is usually separate from the rest of the drive and is only connected to it by means of cables or other suitable (plug-in) connections.
  • the drive preferably further comprises a control device for controlling the motor.
  • the control device can, for example, be designed in the form of a disk and also if it is arranged coaxially to the transmission axis.
  • the drive comprises at least one sensor for detecting a torque and / or a speed, which is connected to the control device in a communicating manner.
  • the sensor is set up to provide a torque and / or a rotary to record the number that are initiated via the retainer shaft.
  • the at least one sensor is preferably arranged radially inside the drive shaft, in particular between the bottom bracket shaft and the drive shaft. If the electric motor is located radially outside the drive shaft, the at least one sensor is shielded from the electric motor by the drive shaft.
  • the drive also includes a housing. At least the swash plate gear and the motor are preferably accommodated in the housing. All essential components of the drive, usually with the exception of the energy source, can also be accommodated in the housing.
  • the housing is preferably essentially cylindrical, the diameter of the cylindrical housing preferably being at most 150 mm, more preferably at most 120 mm, even more preferably at most 100 mm. This results in a particularly space-saving structure of the drive. Due to the cylindrical shape of the housing, the entire drive can be particularly advantageously stored in the frame of a bicycle.
  • At least part of the housing or the entire housing is preferably made of plastic, a plastic composite material or of metal, in particular made of a light metal or a corresponding alloy, for example aluminum or magnesium.
  • a housing made of light metal offers the advantage that it has the necessary rigidity to support the drive components, in particular the gearbox, is light and dissipates the heat generated in the drive well to the outside.
  • the weight of the drive (without energy source) is preferably less than 3.5 kg, preferably less than 3 kg, more preferably less than 2.5 kg.
  • the width of the housing in its axial direction or the axial direction of the Tretla gerwelle is preferably dimensioned such that a Q factor of a maximum of 176 mm is sufficient.
  • a bicycle in particular an e-bike or pedelec, particularly preferably comprises a drive according to the embodiments described above.
  • a bicycle in particular an e-bike or pedelec, particularly preferably comprises a drive according to the embodiments described above.
  • a bicycle preferably further comprises at least one running wheel, at least one pinion or chainring and a traction means running between the running wheel and the at least one pinion, which connects the running wheel to the pinion.
  • a bicycle chain or a toothed belt such as are known in the field of bicycles, can be provided as traction means, for example.
  • the at least one pinion is preferably mounted on the output shaft.
  • the bicycle further comprises a frame which has a substantially tubular receptacle in which the drive is received.
  • Essentially tubular means that the receptacle has the shape of a hollow cylinder.
  • the longitudinal axis of the tubular receptacle is preferably oriented transversely to the longitudinal direction of the frame.
  • the tubular receptacle is preferably formed in the area of a pedal bearing of the bicycle, so that the drive can be used as a pedal bearing drive.
  • the longitudinal axis of the tubular receptacle is then parallel, preferably collinear, to the pedal bearing shaft.
  • a tubular receptacle for the bottom bracket is also seen in conventional bicycles, so that a bicycle according to the invention differs only slightly from conventional bicycles.
  • the tubular shape of the receptacle Due to the tubular shape of the receptacle, it is relatively stiff and yet light. In addition, it enables large-area contact with the cylindrical housing of the drive, thus good heat dissipation from the drive via the housing and the receptacles in the frame of the bicycle, so that the drive can be cooled.
  • the energy source in particular the battery, is preferably arranged coaxially to a down tube or to a seat tube of the frame of the bicycle.
  • the energy source can be integrated into the down tube or the seat tube or can be removed from the frame be trained.
  • the energy source has a housing that was in a state in which it is built into the bicycle, flush with the down tube or the saddle tube. As a result, the energy source can be attached to the bicycle frame in a particularly space-saving manner.
  • a larger energy source can be used and / or the center of gravity can be moved further down.
  • Fig. 1 shows a cross-sectional view of a drive with a Tau mel disc transmission according to the invention according to a first embodiment.
  • Fig. 2 shows a perspective partial sectional view of the swash plate transmission according to the first embodiment.
  • FIG 3 shows a cross-sectional view of a variation of the swash plate transmission according to the first embodiment.
  • FIG. 4 shows a cross-sectional view of a swash plate transmission according to a second embodiment.
  • FIG. 5 shows a cross-sectional view of a swash plate transmission according to a third embodiment.
  • FIG. 6 shows a cross-sectional view of a swash plate transmission according to a fourth embodiment.
  • Fig. 7 shows a side view of a bicycle with a drive comprising the wobble disk drive according to the invention.
  • FIG. 8 shows a side view of the frame of the bicycle according to FIG. 7.
  • a drive 2 with a swash plate gear 4 according to the invention is shown in a cross-sectional view.
  • the drive 2 further comprises a motor 6, a control device 7 for controlling the motor 6, a shaft 8 driven by the motor 6 and an output shaft 10 for driving a vehicle, in particular a bicycle (see FIG. 7).
  • the motor 6 is designed as an electric motor, in particular as an internal rotor electric motor.
  • the control device 7 can, for example, be in the form of a printed circuit board.
  • the swash plate gear 4 comprises a drive shaft which is designed as a hollow shaft.
  • the drive shaft is formed integrally with the shaft 8 driven by the motor 6 and can thus be driven directly by the motor 6.
  • the swash plate transmission 4 comprises an output shaft 12, which is designed as a hollow shaft and defines a transmission axis 14, to which the drive shaft 8 and the output shaft 12 are arranged coaxially.
  • the swash plate gear 4 For power transmission and torque conversion between the drive shaft 8 and the output shaft 12, the swash plate gear 4 comprises a first bevel gear 16, which is arranged coaxially to the gear axis 14, and a first wobble gear 18, which is also designed as a bevel gear, has a first bevel axis 20 and with the first bevel gear 16 meshes.
  • the first wobble gear 18 is mounted on the drive shaft 8 in such a way that the first cone axis 20 is arranged at an angle to the gear axis 14 and intersects this at a wobble point T.
  • At least one of the first bevel gear 16 and the first wobble gear 18 is directed to rotate circumferentially in order to transmit a rotary movement to the output shaft 12.
  • a torque generated by the motor 6 is consequently transmitted from the drive shaft 8 via the swash plate gear 4 and the output shaft 12 to the output shaft 10.
  • the output shaft 12 of the swash plate transmission 4 is connected to the output shaft 10 coupled, in particular in the drive direction of the output shaft 12 and the output shaft 10 connected in a rotationally test manner.
  • the output shaft 10 is set up to drive the vehicle, it preferably has a free shaft section, here a free shaft end 22, on which means for power transmission can be arranged or supported. If the drive 2 z. B. used in a bicycle, at least one pinion or chainring can be placed on the free shaft end, via which a torque from the output shaft 10 by means of a Switzerlandmit means can be transmitted to a wheel of the bicycle (see Fig. 7).
  • the drive 2 further comprises a bottom bracket shaft 24 which is arranged coaxially to the transmission axis 14 and extends through the drive shaft 8 and the output shaft 12.
  • a crank with a pedal can be attached to each of the two ends of the bottom bracket shaft 24, by means of which the bottom bracket shaft 24 can be driven manually.
  • the drive 2 can furthermore have at least one sensor 25 which is connected to the control device 7 in a communicating manner.
  • the at least one sensor 25 can for example be arranged inside or outside a hollow shaft, the speed and / or torque of which it is intended to determine.
  • the at least one sensor 25 is arranged radially inside the drive shaft 8 and radially outside the bottom bracket shaft 24 and is held at this point by means of a web extending from the control device 7 in the axial direction of the transmission axis 14.
  • a plurality of such sensors can also be arranged along the circumference of the shafts 8, 24.
  • the arrangement of the at least one sensor 25 radially inside the drive shaft 8 has the advantage that the at least one sensor 25 is shielded from the motor 6 in this way.
  • the bottom bracket shaft 24 is coupled to the output shaft 10, in particular connected in a rotationally fixed manner at least in the drive direction of the bottom bracket shaft 24 and the drive shaft 10.
  • a first and a second freewheel 26, 28 provided for the non-rotatable connection of the output shaft 12 with the output shaft 10 or the Tretla gerwelle 24 with the output shaft 10.
  • the first freewheel 26 is arranged between the output shaft 12 and the output shaft 10 and couples them to one another.
  • the first freewheel 26 is arranged on an outer jacket surface of the output shaft 10 designed as a hollow shaft and on a peripheral surface of the output shaft 12 designed as a hollow shaft.
  • the second freewheel 28 is arranged between the bottom bracket shaft 24 and the output shaft 10 and couples them together.
  • the second freewheel 28 can be arranged directly between the bottom bracket shaft 24 and the output shaft 10.
  • the output shaft 10 is designed as a hollow shaft and rotatably mounted on the pedal bearing shaft 24 relative to the Tretla gerwelle 24. Because of the second freewheel 28, the output shaft 10 and the bottom bracket shaft 24 are rotatable relative to each other only opposite to the drive direction. The second freewheel 28 could then be arranged between an outer circumferential surface of the T retlagerwelle 24 and an inner circumferential surface of the output shaft 10.
  • the intermediate shaft 30 is designed as a hollow shaft, coaxial with the transmission axis 14 and the pedal gerwelle 24 arranged and rotatably connected to the bottom bracket shaft 24.
  • the intermediate shaft 30 has a shoulder with an enlarged diameter, which extends in the axial direction of the transmission axis 14 to a point radially outside of the output shaft 10.
  • the second freewheel 28 can be arranged between this shoulder of the intermediate shaft 30 and the outer circumferential surface of the output shaft 10. It is understood that ver various other embodiments are conceivable and z. B. can also extend the output shaft 10 radially outside of the intermediate shaft 30 in order to receive the second freewheel 28 between an inner peripheral surface of the output shaft 10 and an outer Mantelflä surface of the intermediate shaft 30.
  • the drive 2 also has a housing 32 in which the components of the drive 2, in particular the motor 6, the control device 7, the swash plate gear 4, the output shaft 10 and the bottom bracket shaft 24 are accommodated.
  • the housing 32 is preferably essentially cylindrical and coaxial with the transmission axis 14.
  • the bottom bracket shaft 24 protrudes on both sides from the housing 32 to allow attachment of the cure and pedals.
  • the output shaft 10 also extends out of the housing 32 to enable at least one pinion or chainring to be attached to the free shaft end 22.
  • the housing 32 can also have a connection option for electrically connecting the motor 6 to an energy source, in particular a rechargeable battery.
  • the housing 32 is preferably formed from a light metal, such as magnesium, for example, as a result of which it has sufficient rigidity for mounting the components of the drive 2 accommodated therein and at the same time has a low weight.
  • the heat generated in the drive 2 can thereby be dissipated to the outside particularly well.
  • Various storage options can be provided in the housing 32, for example for the storage of the retainer shaft 24, one or more of the hollow shafts described herein (e.g. the drive shaft 8, the output shaft 12, the output shaft 10), the bevel and / or wobble gear 16 , 18 of the swash plate gear 4 or of the motor 6 and the control device 7.
  • the retainer shaft 24 one or more of the hollow shafts described herein (e.g. the drive shaft 8, the output shaft 12, the output shaft 10), the bevel and / or wobble gear 16 , 18 of the swash plate gear 4 or of the motor 6 and the control device 7.
  • This swash plate gear 4 um- holds the first bevel gear 16 and the first wobble gear 18.
  • the first bevel gear 16 is fixedly mounted in the housing 32.
  • the first bevel gear 16 is therefore fixed both in the axial direction and in the circumferential direction with respect to the transmission axis 14.
  • the first bevel gear 16 is arranged on the drive side of the first wobble gear 18.
  • the first bevel gear 16 is arranged coaxially to the drive shaft 8, so that its cone axis falls on the gear axis 14.
  • the teeth or tooth tips of the first bevel gear 16 form an outwardly directed, conical surface of the first bevel gear 16.
  • the first wobble gear 18 is also designed as a bevel gear and has the first cone axis 20, which is oriented at an angle to the gear axis 14.
  • the teeth or tooth tips of the first wobble gear 18 form an inwardly directed conical outer surface of the first wobble gear 18. In this way, the first bevel gear 16 and the first wobble gear 18 can mesh with one another.
  • the first wobble gear 18 is mounted on the drive shaft 8 in such a way that the first cone axis 20 is arranged at an angle to the transmission axis 14 and intersects it.
  • the inclination of the first wobble gear 18 or the cone axis 20 is preferably brought about by the mounting of the first wobble gear 18 on the drive shaft 8.
  • the drive shaft 8 preferably has a shaft section 40 which is cylindrical, but is inclined with respect to the gear axis 14 or the central axis of the drive shaft 8.
  • the outer surface of the shaft section 40 is therefore not aligned coaxially to the gear axis 14. Rather, the central or symmetry axis of the shaft section 40 and its lateral surface is inclined by the angle to the Ge gear axis 14, about which the cone axis 20 of the first wobble gear 18 to the transmission axis 14 should be inclined.
  • At least one roller bearing 41 for mounting the first wobble gear 18 on the shaft section 40 of the drive shaft 8 is arranged on the inclined lateral surface of the shaft section 40.
  • the first wobble gear 18 is preferably provided with a first hollow shaft 42 connected or integrally formed at one end of the first hollow shaft 42 in order to support the first hollow shaft 42 simply by means of the roller bearing 41 on the shaft section 40 of the drive shaft 8.
  • the first wobble gear 18 engages in one section with the first bevel gear 16, in FIGS. 1 and 3 in a section below the transmission axis 14. In another section, in particular diagonally In relation to the section in engagement, the first wobble gear 18 is not in engagement with the first bevel gear 16, in FIGS. 1 and 3 above the transmission axis 14.
  • the first wobble gear 18 with the drive shaft 8 is moved around the gear axis 14 in such a way that the first cone axis 20 of the first wobble gear 18 revolves around the gear axis 14 and thereby in the direction of rotation adjoining sections of the toothing of the first bevel gear 16 and the first wobble gear 18 are engaged.
  • the result is the wobbling movement of the first wobble gear 18.
  • a rotational movement of the first wobble gear 18 can then be transmitted to the drive shaft 12 from.
  • the translation can be adjusted via the number of teeth of the first wobble gear 18 and the first bevel gear 16, as already described.
  • the first wobble gear 18 is connected to the output shaft 12 by means of a compensating device 34.
  • the compensation device 34 is set up to compensate for an axial movement component of a wobble movement of the first wobble gear 18 with respect to the transmission axis 14.
  • the compensating device 34 is also set up to transmit a rotary movement from the first wobble gear 18 or the first hollow shaft 42 to the output shaft 12.
  • the compensating device 34 comprises an axially fixed component 36 and an axially movable component 38 connected to the wobble gear 18.
  • the axially fixed component 36 and the axially movable component 38 are consequently relative in the axial direction of the transmission axis 14 movable to each other.
  • the components 36, 38 are preferably not movable relative to one another in order to be able to transmit a rotary movement.
  • the compensating device 34 is designed as a ball joint 34.
  • the axially fixed component 36 is formed by an inner ring or an outer ring of the ball joint 34, while the axially movable component 38 is formed by the other of the inner ring and outer ring of the ball joint 34.
  • a plurality of axially extending grooves are provided along the circumference in each case.
  • One groove on the inner surface of the outer ring and one groove on the outer surface of the inner ring are aligned with one another and form an axial guide in which a rolling element 39, in particular a ball, is received between the inner ring and the outer ring.
  • the grooves are dimensioned such that the inner ring and the outer ring are movable relative to one another at least by the amount of the axial displacement of the first wobble gear 18 in the axial direction.
  • the grooves are preferably dimensioned such that the balls cannot move within the grooves in the circumferential direction of the outer ring and the inner ring.
  • the outer ring and the inner ring are therefore essentially fixed to one another or non-rotatably connected to one another in the circumferential direction.
  • the outer ring of the ball joint 34 is fixedly connected to the first wobble gear 18 and thus forms the axially movable component 38, while the inner ring of the ball joint 34 is fixedly connected to the output shaft 12 and the axially fixed Component 36 forms.
  • FIG. 3 shows a variant of the first embodiment in which the compensating device 34 or the ball joint 34 is designed differently from the variant according to FIGS. 1 and 2. Otherwise, the embodiment according to FIG. 3 corresponds to the embodiment according to FIGS. 1 and 2.
  • the outer ring of the ball joint 34 is firmly connected to the output shaft 12 and forms the axially fixed component 36, while the inner ring of the ball joint 34 is fixed to the first wobble gear 18 is connected and the axially movable component 38 forms.
  • a particularly simple structure is obtained when the outer ring and the inner ring of the ball joint 34 are each formed integrally with the first wobble gear 18 and the output shaft 12, respectively.
  • the first hollow shaft 42 can correspondingly be designed as an outer ring or inner ring of the ball joint 34 at an end opposite the first wobble number wheel 18.
  • the output shaft 12 can also be designed as an inner ring or outer ring of the Ku gel joint 34 at an end facing the wobble gear 18.
  • Fig. 3 the gear cone angle ⁇ of the first bevel gear 16 and the first wobble gear 18, the tooth angle d of the first bevel gear 16 and the first wobble gear 18, and the wobble angle g of the first wobble gear 18 are shown.
  • the definition of the gear cone angle ⁇ and the tooth angle d applies accordingly to all wobble and bevel gears described here.
  • the definition of the wobble angle g applies accordingly to all wobble gears described here.
  • the gear cone angle bk of the first bevel gear 16 is defined as the angle between a first axis 43, which is perpendicular to the cone axis of the first bevel gear 16 or to the transmission axis 14, and a surface line of the first bevel gear 16, which is formed by the tips of its teeth is.
  • the gear cone angle bt of the first wobble gear 18 is defined as the angle between a second axis 45, which is perpendicular to the first cone axis 20 of the first wobble gear 18, and a surface line of the first wobble gear 18, which is formed by the tips of its teeth.
  • the first bevel gear 16 and the first wobble gear 18 preferably have a gear cone angle bk, bt which is between 10 ° and 60 °, preferably between 15 ° and 40 °, more preferably between 20 ° and 35 °.
  • bk gear cone angle
  • bt gear cone angle
  • the two Zahnradke gelwinkel b k , bt are equal.
  • the first and second axes 43, 45 intersect the transmission axis 14 at the wobble point T.
  • the wobble point T is defined as the pivot point of the wobble gear 18 and lies on the transmission axis 14.
  • the wobble point T is arranged in a stationary manner.
  • the wobble angle g is defined between the first axis 43, which is aligned perpendicular to the transmission axis 14 at the wobble point T, and a maximum deflection of the first wobble gear 18 in the direction of the drive (positive sign) or in the direction of the output (negative sign).
  • the wobble angle g can be specified as the angle between the first cone axis 20 of the first wobble gear 18 and the transmission axis 14 and accordingly have a positive or negative sign.
  • the first wobble gear 18 preferably has a wobble angle g between +/- 1 ° and +/- 6 °, preferably between +/- 1.5 ° and +/- 4 °, preferably between +/- 2 ° and + / - 3.5 °.
  • Each tooth tip and each tooth base of the teeth of the first bevel gear 16 and the first wobble gear 18 preferably extends on a straight line through the wobble point T.
  • a tooth angle dk of the first bevel gear 16 or a tooth angle dt of the first wobble gear 18 is defined between the straight line one Tooth tip and the straight line of a tooth base of a tooth of the respective (bevel or wobble) gear 16, 18.
  • the tooth angle dk, dt is preferably between 1 ° and 10 °, preferably between 2 ° and 5 °.
  • this can also have at least one balancing mass 44 to compensate for vibrations. Vibrations are induced in particular by the components that are not arranged rotationally symmetrically to the transmission axis, such as the first wobble gear 18, the shaft section 40, the roller bearing 41 and the hollow shaft 42.
  • the balancing mass 44 is preferably attached to or integrally formed with the shaft 8 driven by the motor 6, in particular the drive shaft 8, and counteracts an oscillation or imbalance induced by the wobbling movement of the first wobble gear 18 The shift in the center of gravity during one revolution of the first wobble gear 18 can essentially be compensated for by the balancing mass 44.
  • a plurality of balancing masses 44 can also be provided at different points in the axial direction and in the circumferential direction.
  • the arrangement of the at least one balancing mass 44 on an inner circumferential surface of the drive shaft 8 is preferred, since sufficient installation space is available at this point.
  • a second embodiment of the swash plate gear 4 is shown in a cross-sectional view. This swash plate gear 4 comprises the drive shaft 8, the first bevel gear 16, the first swash gear 18 and the output shaft 12.
  • the swash plate gear 4 according to the second embodiment differs from the first embodiment according to FIGS is set in the axial direction as well as in the circumferential direction with respect to the output shaft 12. It is preferred that the first bevel gear 16 is formed integrally with the output shaft 12, as shown in FIG. 4. The first bevel gear 16 is arranged on the output side of the first wobble gear 18 and aligned in the direction of the first wobble gear 18 and thus in the direction of the drive.
  • the first wobble gear 18 is aligned in the direction of the output in order to mesh with the first bevel gear 16.
  • the first wobble gear 18 is preferably formed integrally with a first hollow shaft 42 which, analogously to the first embodiment, is supported by means of a roller bearing 41 on a shaft section 40 of the drive shaft 8, which controls the inclination of the first conical axis 20 of the first wobble gear 18 with respect to the transmission axis 14 causes.
  • FIGS. 1 to 3 which apply accordingly to the second embodiment.
  • the compensation device 34 for compensating for a movement component of the wobble movement of the first wobble gear 18 which is axial with respect to the transmission axis 14 is arranged in the second embodiment between the first wobble gear 18 and the housing 32.
  • the axially fixed component 36 is firmly connected to the housing 32, in particular in the axial direction and in the circumferential direction on the housing 32 Festge sets.
  • the axially movable component 38 is fixedly connected to the first wobble gear 18 a related party.
  • the movable component 38 is preferably formed integrally with the first hollow shaft 42 at an end thereof opposite the wobble gear 18.
  • the compensating device 34 can also be designed as a ball joint.
  • the inner ring is then, analogously to FIG. 3, integral with the first th hollow shaft 42 is formed.
  • the outer ring of the ball joint 34 is placed firmly on the housing 32.
  • the first wobble gear 18 in the second embodiment cannot rotate about the transmission axis 14. Rather, the first wobble gear 18 can only move in the axial direction and pivot back and forth in the circumferential direction about the balls 39 of the ball joint 34.
  • the superimposition of the movement of the first wobble gear 18 in the axial direction and the pivoting of the first wobble gear 18 about the balls 39 results in an essentially elliptical movement of the first wobble gear 18.
  • the first wobble gear 18 meshes with the first bevel gear 16 during part of the elliptical movement and a force or movement is transmitted in the drive or circumferential direction to the first bevel gear 16 and thus into the output shaft 12 initiated. During the further movement, the engagement is gradually released and the wobble gear 18 is moved against the drive direction. Then it approaches the bevel gear 16 again, gradually engages with it and again transmits a force in the drive direction.
  • the input shaft 8 and the output shaft 12 can rotate in opposite directions.
  • a third embodiment of the swash plate gear 4 according to the invention is shown in a cross-sectional view.
  • the embodiment according to FIG. 5 differs from the embodiments described above essentially in that the swash plate gear 4 additionally has a second bevel gear 46 and a second Swash gear 48 includes.
  • a compensation device is not required in this embodiment.
  • the first bevel gear 16 is firmly connected to the output shaft 12, is arranged on the output side of the first wobble gear 18 and faces it.
  • the first wobble gear 18 is aligned in the direction of the first bevel gear 16 analogously to the second embodiment according to FIG with respect to the transmission axis 14 causes.
  • the second bevel gear 46 is fixedly mounted in the housing 32, in particular fixed in the housing 32 both in the axial direction and in the circumferential direction.
  • the second bevel gear 46 is arranged on the output side of the second wobble gear 48 and aligned in the direction of the drive.
  • the second wobble gear 48 is fixedly connected to the first wobble gear 46, preferably set in front of the first wobble gear 18 both in the axial direction and in the circumferential direction.
  • the first and the second wobble gear 46, 48 are arranged coaxially, so that a second cone axis of the second wobble gear 48 coincides with the first cone axis 20.
  • the first and second wobble gears 18, 48 are oriented in the same direction.
  • the two wobble gears 18, 48 are designed separately from one another and then connected to one another, e.g. B. screwed, pressed or connected by means of any shaft-hub connection.
  • a first hollow shaft 42 which is integrally formed with the first or second wobble gear 18, 48 is particularly advantageous.
  • the other of the first and second wobble gears 18, 48 formed separately and attached to the first hollow shaft 42 to close.
  • the first hollow shaft 42 can be mounted on the shaft section 40 by means of the roller bearings 41.
  • the direction of rotation of the output shaft 12 can be opposite to the direction of rotation of the drive shaft 8.
  • a fourth embodiment of the swash plate mechanism 4 according to the invention is shown in a cross-sectional view.
  • the swash plate gear 4 additionally comprises a second bevel gear 46 and a second swash gear 48.
  • a compensation device 34 is not required.
  • the first bevel gear 16 is firmly connected to the output shaft 12, in particular formed integrally with it.
  • the embodiment according to FIG. 6 differs from the embodiment according to FIG. 5 essentially in that the first wobble gear 18 and the second wobble gear 48 are oriented in opposite directions and the second bevel gear 46 is therefore mounted in the housing 32 on the drive side. Otherwise, the description of the third embodiment also applies analogously to the fourth embodiment.
  • the first wobble gear 18 and the second wobble gear 48 are firmly connected to one another, in particular set to one another both in the axial direction and in the circumferential direction.
  • the first and the second wobble gear 46, 48 are arranged coaxially, so that a second cone axis of the second wobble gear 48 coincides with the first cone axis 20. Due to the orientation in opposite directions, it is also possible and preferred to form the first wobble gear 18 and the second wobble gear 48 integrally with the first hollow shaft 42.
  • the first and second wobble gears 18, 48 can, however, also be formed separately and connected to the first hollow shaft 42.
  • the first wobble gear 18 is oriented in the direction of the output and there faces the first bevel gear 16.
  • the second wobble gear 48 is aligned in the direction of the drive.
  • the second bevel gear 46 is arranged on the drive side of the second wobble gear 48 and faces it in order to engage with the second wobble gear 48.
  • the second bevel gear 46 is fixedly connected to the housing 32, preferably fixed both in the axial direction and in the circumferential direction.
  • the first bevel gear 16 and the first wobble gear 18 mesh with one another in a portion which is arranged diagonally to the portion in which the second bevel gear 46 and the second wobble gear 48 mesh with one another.
  • the output shaft 12 can rotate in the opposite direction to the drive shaft 8.
  • the drive shaft is preferably by means of a roller bearing 49, for. B. a ball or needle bearing, mounted on the bottom bracket shaft 24.
  • a bicycle 50 with a drive 2 with a wobble disk transmission 4 is shown in a side view.
  • the bicycle 50 comprises a preferably spring-loaded frame 52, at least one wheel 54 and a traction mechanism 56 for connecting the driving wheel 54 to the drive 2.
  • a conventional bicycle 50 has a front wheel 54 and a rear wheel 54, the rear wheel being the driving wheel 54 forms.
  • One or more pinions or chain rings 58 can be mounted on the output shaft 10.
  • the traction means 56 transmits a rotary movement or a force from the pinion 58 to the running wheel 54.
  • the traction means 56 can be formed, for example, as a bicycle chain or toothed belt.
  • cranks 60 and pedals 62 for manually driving the bicycle 50 via the bottom bracket shaft 24 and the output shaft 10.
  • FIG. 8 the frame 52 of the bicycle 50 according to FIG. 7 is shown in a side view.
  • the frame 52 comprises a tubular receptacle 64 in which the drive 2, in particular its cylindrical housing 32 (see FIG. 1), can be received.
  • the outer diameter of the cylindrical housing 32 therefore preferably corresponds to the inner diameter of the tubular receptacle 64.
  • the tubular receptacle 64 is preferably designed to be closed along its circumference, as a result of which the frame 52 is also particularly rigid in the area of the receptacle 64 and thus in the area of the bottom bracket.
  • the receptacle 64 can be thin-walled be formed, whereby the frame 52 is lighter overall. Due to the small dimensions of the drive 2 and the receptacle 64, the design freedom of the frame 52, in particular in the area of the bottom bracket, is greater.
  • the cylindrical housing 32 can be in contact with the tubular receptacle 64 along the entire circumference with its jacket surface, as a result of which good heat transfer from the housing 32 into the frame 52 is made possible.

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  • General Engineering & Computer Science (AREA)
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Abstract

L'invention concerne une transmission à plateau oscillant (4) comprenant : un arbre d'entraînement (8) qui se présente sous la forme d'un arbre creux et qui peut être entraîné par une source d'alimentation ; un arbre de sortie (12) qui se présente sous la forme d'un arbre creux et définit un axe de transmission (14), avec lequel l'arbre d'entraînement (8) est agencé de manière coaxiale ; un premier engrenage conique (16) qui est agencé de manière coaxiale avec l'axe de transmission (14) ; un premier engrenage oscillant (18) qui se présente sous la forme d'un engrenage biseauté présentant un premier axe de biseau (20) et s'engrène avec le premier engrenage biseauté (16), le premier engrenage oscillant (18) étant monté sur l'arbre d'entraînement (8) de sorte que le premier axe de biseau (20) du premier engrenage oscillant (18) soit agencé de manière oblique par rapport à l'axe de transmission (14) et coupe ledit axe ; au moins l'un parmi le premier engrenage biseauté (16) et le premier engrenage oscillant (18) étant conçu pour tourner en continu afin de transmettre un mouvement rotatif à l'arbre de sortie (12). Le premier engrenage oscillant (18) présente un angle d'oscillation qui est compris entre +/- 1° et +/- 10°.
PCT/EP2021/052141 2020-02-06 2021-01-29 Transmission et entraînement auxiliaire pour une bicyclette WO2021156149A1 (fr)

Applications Claiming Priority (2)

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DE102020103026.6A DE102020103026A1 (de) 2020-02-06 2020-02-06 Getriebe und Hilfsantrieb für ein Fahrzeug

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WO2023116409A1 (fr) * 2021-12-22 2023-06-29 姜虹 Réducteur à engrenage de nutation

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EP1934082A1 (fr) * 2005-10-06 2008-06-25 ThyssenKrupp Presta AG Direction a superposition dotee d'un plan de retour mecanique
EP2672147A2 (fr) 2009-03-30 2013-12-11 Clean Mobile AG Véhicule avec unité moteur-engrenage
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US20170191549A1 (en) * 2016-01-06 2017-07-06 The Boeing Company Elliptically interfacing gearbox
DE112016002380T5 (de) 2015-05-25 2018-02-15 Thk Co., Ltd. Drehzahlreduktions- oder Drehzahlerhöhungsvorrichtung

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GB976608A (en) * 1962-09-10 1964-12-02 Papst Hermann Swash-plate mechanism for internal combustion engines
DE2162867A1 (de) 1970-12-17 1972-07-06 Ishida T Bewegungsübertragungsmechanismus
DE19748201C1 (de) * 1997-10-31 1999-03-04 Alber Ulrich Gmbh Nabenantriebsvorrichtung
EP1025372A1 (fr) * 1997-10-31 2000-08-09 Lucas Industries Public Limited Company Systeme de freinage pour vehicule routier
DE19934161A1 (de) * 1999-07-21 2001-02-08 Lucas Automotive Gmbh Taumelscheibengetriebe und Getriebemotor
DE10355259A1 (de) * 2003-11-26 2005-06-23 Robert Bosch Gmbh Taumelgetriebe
EP1934082A1 (fr) * 2005-10-06 2008-06-25 ThyssenKrupp Presta AG Direction a superposition dotee d'un plan de retour mecanique
EP2672147A2 (fr) 2009-03-30 2013-12-11 Clean Mobile AG Véhicule avec unité moteur-engrenage
AT514272B1 (de) * 2013-06-06 2015-10-15 Gharehgozloo Parastu Mag Antriebseinheit und Fahrzeug
DE102014016719A1 (de) 2014-11-13 2016-05-19 Ali Dastrandj Antriebseinheit und Fahrzeug
DE112016002380T5 (de) 2015-05-25 2018-02-15 Thk Co., Ltd. Drehzahlreduktions- oder Drehzahlerhöhungsvorrichtung
US20170191549A1 (en) * 2016-01-06 2017-07-06 The Boeing Company Elliptically interfacing gearbox

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023116409A1 (fr) * 2021-12-22 2023-06-29 姜虹 Réducteur à engrenage de nutation
US11933385B2 (en) 2021-12-22 2024-03-19 Hong Jiang Nutation reducer

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