TWI791022B - Transmission for a bicycle - Google Patents

Abstract

Transmission for a bicycle, including an input formed by a crank axle, and an output connectable to a front sprocket of the bicycle, a housing connectable or connected to a frame of the bicycle, a planetary gear set having at least three rotational members, wherein a first rotational member is connected to the crank axle, a second rotational member is connected to the output and a third rotational member is connected to the housing, a sensor between the third rotational member and the housing, and an electric motor with a stator connected to the housing and a rotor connected to the output, wherein the third rotational member is formed by a planet carrier.

Description

Transmission mechanism for bicycles

The present invention relates to a transmission mechanism for a bicycle.

The present invention relates to a transmission mechanism for a bicycle. The transmission may comprise: - an input formed by a crankshaft and an output connectable to a front sprocket of the bicycle, - a housing connected or connectable to a frame of the bicycle, - having a first planetary gear set of at least three rotating members, wherein a first rotating member is connected to the crankshaft, a second rotating member is connected to the output, and a third rotating member is connected to the housing, - a sensor interposed between the third rotating member and the housing, and - an electric motor having a stator connected to the housing and a rotor connected to the output.

The sensor may be a force sensor, a position sensor or a displacement sensor, such as a rotation sensor. From a measured sensor value the torque transmitted to the housing can be calculated. The electric motor is used to support the cyclist. Also, a control unit can control the electric motor according to the calculated torque.

Such a transmission is known from DE 10 2011 089559 A. In electric bicycles, a direct drive motor is used either at the front wheel or at the rear wheel. Rear hub motor provides optimum drivability. One of the disadvantages of rear hub motors is that geared hubs cannot be used. It is possible to use a derailleur. However, in the case of deceleration on an incline, the torque that the electric motor can apply directly to the wheels remains the same, and what is actually desired is a higher supporting torque from the motor. To solve this problem, an electric motor can be connected to the crankshaft, as in known transmissions. Therefore, gear hubs and derailleurs can be used at the same time. A further advantage is that, in the case of deceleration, the torque of the electric motor is multiplied towards the rear wheels.

A common chain drive mechanism reduces the torque sent to the rear wheel by two times, and a common gear hub can multiply the torque by up to two times. Thus, the torque of the electric motor directly coupled to the crankshaft is not multiplied towards the rear wheels as is often the case in the lowest gear. To solve this problem, the size of the front sprocket can be reduced twice, which results in twice the torque from the electric motor at the rear wheel. However, this triples the rotational speed of the front sprocket and requires reduced transmission between the front sprocket and the crankshaft (thus increasing from the crankshaft to the front sprocket). A concentric transmission is useful for this, such as a planetary gear set.

Because crankshaft torque (not motor torque) requires a torque measurement, it is also well suited to equip planetary gear sets for measuring torque by force on a stationary (non-rotating) rotating member.

When the ring disc is fixed, the planetary carrier is connected to the input, and the sun gear is connected to the output, it is difficult to construct a double planetary gear set, as is the case in known transmissions, because the transmission between the ring disc and the sun disc is then must be equal to one, that is, the diameter of the annular disk must be equal to the diameter of the solar disk. Furthermore, when the derailleur or hub drive does not have direct or sufficiently precise control related to the torque of the electric motor, it can be difficult to control the output torque.

An object is to provide a transmission as described above, wherein, in a simpler manner than known transmissions, a first planetary gear set can be used with a larger Transmission ratio (preferably equal to or greater than 2) to build.

Also, the transmission mechanism is characterized in that the third rotating member is formed by a planet carrier.

Optionally, at least a part of the third rotating member is part of the housing.

Optionally, one or more planet shafts are connected to the planet carrier and/or housing.

Optionally, the sensor is connected to the carrier, and/or the housing, and/or one or more of the planet shafts.

With a planetary gear set having double planets, a transmission ratio between the ring disc and the sun disc must be two (or more) (increasing speed towards the sun disc), which can be suitably constructed, for example, with a connection to The ring disk of the input and the sun disk connected to the output are constructed. The output speed will be higher than the input speed. Again, this is also possible with a planetary gear set having either two sun gears or two ring gears, and a planet carrier. In both configurations, the pedaling torque can be measured by measuring the torque on the stationary planet carrier, or on the planet shaft(s) attached to the housing, or on the housing connected by a shaft therein.

Optionally, the transmission is configured such that the second rotating member is formed by a sun gear.

Optionally, the transmission is configured such that the first rotating member is formed by a further sun gear.

Optionally, the transmission is configured such that the first rotating member is formed by a ring gear.

Optionally, the planet carrier includes a plurality of planet gear pairs. Each pair of the planetary gears is rotatably coupled. The planetary gears of each pair can mesh with each other. One of the meshing planetary gears of the pair may mesh with the ring gear. The other of the meshing planetary gears of the pair may mesh with the sun gear. The planetary gears of each pair can be rotatably fixed in a coaxial manner. One of the rotationally fixed planetary gears of the pair can mesh with the sun gear. The other of the rotationally fixed planetary gears of the pair can mesh with the further sun gear.

These known transmissions may have the further disadvantage that the electric motor rotates at a high rotational speed and is coupled to the crankshaft or chain ring via one or more toothed gears. This causes sound to be produced.

According to an aspect, the transmission may be configured such that the electric motor train is directly connected to the crankshaft or chain ring. Therefore, the electric motor can rotate at a low rotational speed without toothed gears interposed between the electric motor and the crankshaft or the chain ring. However, the invention is not limited to the direct connection of the electric motor to one of the chainrings.

According to yet another aspect, a sub-transmission mechanism is integrated in the transmission mechanism. With this additional sub-gear, the speed ratio between crank and wheel can be adjusted. A further advantage is that the crankshaft, electric motor, sub-gear and torque sensor can all be integrated in one housing that can be mounted to the bicycle frame and no further hub drive or derailleur system is required. However, it is still possible to combine a hub/wheel drive and/or derailleur with the system.

Optionally, the sub-gear includes a torque transmitting element, and at least one sub-gear input and one sub-gear output. The sub-transmission input can be connected to the output of the first planetary gear set, and the sub-transmission output can be connected to the input of a chain/belt drive of the bicycle, for example, to the front sprocket.

Optionally, the sub-transmission is embodied as a one-step gear transmission.

Optionally, the sub-transmission mechanism is embodied as a continuously variable transmission mechanism.

Optionally, the sub-transmission is embodied as a second planetary gear set having at least three rotating members, wherein a first rotating member is connected to the output of the first planetary gear set and a second rotating member is connected to The input to the chain/belt drive, and a third rotating member is connected to a torque reaction element, such as a housing and/or an electric motor.

According to yet another aspect, the sub-transmission is embodied as a second planetary gear set, and the electric motor is connected to one of the rotating members of the second planetary gear set.

Optionally, the electric motor is connected to the third rotating member of the second planetary gear set.

Optionally, a first clutch and/or a first flywheel are connected between the third rotating member of the second planetary gear set and the housing.

Optionally, a second clutch and/or a second flywheel are connected between the rotating members of the second planetary gear set.

Optionally, the first rotating member of the second planetary gear set is a sun gear. Optionally, the second rotating member of the second planetary gear set is a planet carrier. Optionally, the third rotating member of the second planetary gear set is a ring/ring gear.

One advantage is that the power input by the crank will be amplified towards the wheels as the bicycle speed is increased by the electric motor above a certain wheel speed. This will enable the bicycle to have a constant high acceleration with a constant low input torque and speed. This will give the rider a sense of progressive acceleration.

Optionally, a selectable fixed gear ratio can be applied with the second planetary gear set using the first clutch/freewheel and/or the second clutch/freewheel.

Optionally, an overrunning bearing or an overrunning clutch is connected between the crankshaft and the first rotating member of the first planetary gear set, and/or the output and the second rotating member of the first planetary gear set components, and/or between the output and the electric motor.

Optionally, the output is formed by a hollow shaft. Optionally, the hollow output shaft is concentric with the crankshaft.

Optionally, the sensor includes one or more of a force sensor, a position sensor, a displacement sensor, and a rotation sensor.

Optionally, the transmission comprises a calculation unit configured for calculating the torque transmitted to the housing on the basis of a measurement value of the sensor.

According to an aspect, a bicycle is provided, which includes one of the transmission mechanisms described above.

Optionally, the bicycle comprises a control unit configured for controlling the electric motor depending on the measured sensor value and/or the calculated torque.

According to an aspect, a method is provided that uses a sensor to determine a torque applied to a crankshaft of a bicycle. The sensor is disposed between a third rotating member and a housing of a transmission having an input formed by the crankshaft and connected to a front sprocket and/or chain ring of the bicycle Connected to an output, the housing is connected to a frame of the bicycle. The transmission has a first planetary gear set having at least three rotating members, wherein a first rotating member is connected to the crankshaft, a second rotating member is connected to the output, and the A third rotating member is connected to the housing, the transmission mechanism also has an electric motor having a stator connected to the housing, and a rotor connected to the output, wherein the third rotating member is driven by a planetary frame formed. The method further includes determining the torque based on a measurement of the sensor. The sensor may be configured to measure one or more of force, position, displacement, and rotation.

According to an aspect, a method for supporting a cyclist is provided. The method includes determining a torque applied by the cyclist to a crankshaft of a bicycle, as described above. The method also includes controlling the electric motor of the bicycle based on the calculated torque.

It will be appreciated that any one or more of the above aspects, features and options may be combined. It will be appreciated that any one option described in view of one of these aspects may apply equally to any other aspect. It will also be clear that in view of the transmission all aspects, features and options described apply equally to the bicycle and the methods and vice versa.

FIG. 1 shows a schematic representation of a transmission mechanism 1 . The transmission 1 includes an input, here formed by a crankshaft 3 . The transmission mechanism 1 includes an output 5 . In this example, the output 5 is connected to a front sprocket 7 of a bicycle. Here, the front sprocket 7 is coupled to a rear sprocket 11 via a chain or belt 9 . Here, the rear sprocket 11 is coupled to a hub 15 via an overrunning bearing 13 .

In this example, the crankshaft 3 is connected to a planetary gear set 19 via a second overrunning bearing 17 . It will be appreciated that it is also possible that the second overrunning bearing 17 is alternatively coupled between the planetary gear set 19 and the output 5 . Planetary gear set 19 includes three rotating members. A first rotating member 21 is connected to the crankshaft. A second rotating member 23 is connected to the output 5 . A third rotating member 25 is connected to a housing (not shown in FIG. 1 ) which is connected to a bicycle frame 27 (schematically shown).

In order to measure the torque applied to the crankshaft 3 via the pedal 31, a torque sensor 29 is installed between the third rotating member 25 and the housing. Furthermore, for example, an electric motor 33 is included in the housing. The electric motor 33 is coupled to the output 5 via a third overspeed bearing 35 . The electric motor train is configured to support a cyclist. Also, a control unit (not shown) here controls the electric motor according to the torque measured by the torque sensor 29 .

FIG. 2 shows a simplified schematic representation of a cross-sectional view of a transmission mechanism 1 according to FIG. 1 . Here it can be clearly seen that the stator 39 of the electric motor 33 is connected to the casing 37 and the rotor 41 of the electric motor 33 is connected to the output 5 via the third overspeed bearing 35 . The rotor 41 is received in the housing 37 via bearings 43 . Crankshaft 3 is received in housing 37 via bearing 45 and bearings 47 and 49 . Here, the output 5 is formed by a hollow shaft received between bearings 47 and 49 . In this example, the third rotating member 25 is formed by a planet carrier PC. In this example, the second rotating member 23 is formed by the sun gear S1. In this example, the first rotating member 21 is formed by yet another sun gear S2.

In the example of FIG. 2 , the planet carrier PC is connected to the housing 37 . Therefore, the planet carrier PC is at rest. Here, the sun gear S1 is connected to output 5. Here, a further sun gear S2 is connected to the crankshaft 3 . Here, the planet carrier PC includes one or more planetary gear pairs P1, P2. Each pair of planetary gears P1, P2 is rotationally coupled. Here, the planetary gear trains of the respective pairs are coaxially coupled. In this example, the first planetary gear P2 of the pair meshes with the further sun gear. Here, the second planetary gear P1 of the pair meshes with the sun gear S1.

FIG. 3 shows a modular variant of a transmission mechanism 1 according to FIG. 1 . The housing 37 comprises two parts 37a, 37b. The first housing portion 37a is connected to the frame 27 . The second housing portion 37b covers the bearing 49 . The first and second housing parts 37a, 37b may be connected to each other eg by means of fasteners such as bolts. In this example, the rotor 41 comprises two parts 41a, 41b. Here, the first rotor part 41 a is connected to the magnet 42 . Here, the second rotor part 41 b is connected to the third overspeed bearing 35 . In this example, the first and second rotor parts 41a, 41b are connected by a splined connection 51 . The splined connection 51 includes a first splined connection portion 51a and a second splined connection portion 51b. Therefore, the first and second rotor parts 41a, 41b can be connected and disconnected in a sliding manner.

In FIG. 4, the transmission mechanism is divided into a first transmission module 1a and a second transmission module 1b. Here, the first transmission module 1a includes a first housing portion 37a, a first rotor portion 41a and a first spline connection portion 51a. Here, the second transmission module 1b includes a second housing portion 37b, a second rotor portion 41b and a second spline connection portion 51b. Here, the first transmission module 1 a includes a torque sensor 29 and a bearing 45 . Here, the second transmission module 1 b includes a crankshaft 3 and a hollow output shaft 5 . Moreover, in this example, the second transmission module 1b includes a planet carrier PC, a pair of planetary gears P1, P2, a sun gear S1, and another sun gear S2. A coupling member 53 is included between the torque sensor 29 and the third rotating member (here, the planet carrier PC). The coupling 53 is configured such that the sliding of the second transmission module 1b into the first transmission module 1a will rotationally couple the parts 53a, 53b of the coupling 53 comprised by the first and second transmission modules, respectively. Similarly, sliding the second transmission module 1 b out of the first transmission module 1 a will decouple the coupling 53 .

FIG. 5 shows one of the variants of the transmission 1 according to FIG. 1 in the individual modules 1a, 1b. Here, the first transmission module 1a includes a first housing portion 37a, a first rotor portion 41a and a first spline connection portion 51a. Here, the second transmission module 1b includes a second housing portion 37b, a second rotor portion 41b and a second spline connection portion 51b. Here, the second transmission module 1 b includes a crankshaft 3 and a hollow output shaft 5 . Moreover, in this example, the second transmission module 1b includes a planet carrier PC, a pair of planetary gears P1, P2, a sun gear S1, and another sun gear S2. In this example, the second transmission module 1 b includes a torque sensor 29 and a bearing 45 . Here, the second transmission module 1 b includes an auxiliary component 54 . The auxiliary member 54 may be connected to the first housing portion 37a, for example, via a splined connection 56 . Next, the first transmission module 1a includes a first spline connection portion 56a, and the second transmission module 1b includes a second spline connection portion 56b.

FIG. 6 shows a simplified schematic representation of a cross-sectional view of a transmission mechanism 55 . In this transmission mechanism 55 , the electric motor 33 is not arranged concentrically but centrifugally with respect to the crankshaft 3 . Here, the rotor 41 is connected to the third overspeed bearing 35 via a secondary transmission 57 . The secondary transmission mechanism 57 can be any type of transmission mechanism, such as a gear plate transmission mechanism, chain transmission mechanism and/or chain belt transmission mechanism.

FIG. 7 shows a schematic representation of a transmission mechanism 59 . In the transmission 59, the planetary gear set 19' is different. Here, the planetary gear set 19' includes a sun gear S and a ring gear R instead of two sun gears S1, S2 and a planet carrier PC. The planetary gears Pa and Pb are provided between the sun gear S and the ring gear R as a pair.

FIG. 8 shows a simplified schematic representation of a section of a transmission mechanism 59 according to FIG. 7 . The first rotating member 21' of the planetary gear set 19' is here formed by a ring gear R. The second rotating member 23' of the planetary gear set 19' is here formed by a sun disk S. The third rotating member 25' of the planetary gear set 19' is here formed by a planet carrier PC to which the planet gears Pa, Pb are connected in pairs. The torque sensor 29 ′ is here placed against the stator 39 and not against the housing 37 .

In Figures 9 and 10, two examples of transmission mechanisms in separate modules are shown, with torque sensors 29 in different positions.

In FIG. 9, the transmission mechanism 59 includes a first transmission module 59a and a second transmission module 59b. The first housing portion 59a is connected to the frame 27 . The second housing portion 59b covers the bearing 49 . The first and second housing parts 59a, 59b may be connected to each other eg by fasteners such as bolts. In this example, the rotor 41 comprises two parts 41a, 41b. The first rotor part is for example connected to a magnet. Here, the second rotor part 41 b is connected to the third overspeed bearing 35 . In this example, the first and second rotor parts 41a, 41b are connected by a splined connection 51 . The spline connection 51 includes a first spline connection part and a second spline connection part. Therefore, the first and second rotor parts 41a, 41b can be connected and disconnected in a sliding manner. Here, the first transmission module 59a includes a first housing portion 37a, a first rotor portion 41a and a first spline connection portion. Here, the second transmission module 59b includes a second housing portion 37b, a second rotor portion 41b and a second spline connection portion. Here, the second transmission module 59b includes the crankshaft 3 and the hollow output shaft 5 . Moreover, in this example, the second transmission module 59b includes a planetary carrier PC, planetary gears Pa, Pb, and a sun gear S. In this example, the second transmission module 59 b includes the torque sensor 29 and the bearing 45 . In FIG. 9 the torque sensor 29 ′ is placed against the stator 39 . Here, the second transmission module 59b includes an auxiliary member 54'. The auxiliary member 54' may be connected to the first housing portion 37a, for example, via a splined connection. Next, the first transmission module 59a includes a first spline connection portion, and the second transmission module 59b includes a second spline connection portion.

In Fig. 10, the transmission mechanism 59' includes a first transmission module 59a' and a second transmission module 59b'. In FIG. 10, the first transmission module 59'a includes the first housing portion 37a, the first rotor portion 41a, and the first splined connection portion 51a. Here, the second transmission module 59'b includes the second housing part 37b, the second rotor part 41b and the second spline connection part 51b. Here, the first transmission module 59'a includes the torque sensor 29 and the bearing 45. In FIG. 10 the torque sensor 29 ′ is placed against the housing 37 . Here, the second transmission module 59'b includes the crankshaft 3 and the hollow output shaft 5. Moreover, in this example, the second transmission module 59'b includes a planetary carrier PC, planetary gears Pa, Pb, and a sun gear S. A coupling member 53' is included between the torque sensor 29 and the third rotating member (here, the planet carrier PC). The coupling 53' is configured such that sliding the second transmission module 59'b into the first transmission module 59'a will rotationally couple the coupling 53' comprised by the first and second transmission modules, respectively. Parts 53'a, 53'b. Similarly, sliding the second drive module 59'b out of the first drive module 59'a will decouple the coupling 53'.

FIG. 11 shows a schematic representation of a transmission mechanism 60 . The transmission mechanism 60 includes a first planetary gear set 19 , for example as described with reference to FIGS. 1 to 10 . In FIG. 11 , the transmission mechanism 60 further includes a sub-transmission mechanism 61 . The sub-gear 61 includes torque transfer elements, and at least one sub-gear input 62 and one sub-gear output 63 . Here, the sub-transmission input 62 is connected to the output 5 of the first planetary gear set 19 . Here, the sub-transmission output 63 is connected to the input of the chain/belt drive 9 of the bicycle, eg to a front sprocket. The chain/belt drive 9 is coupled to a hub 15 via an overspeed bearing (not shown). In the example of FIG. 11 , the electric motor 33 is connected to a second input 64 of the sub-transmission 61 . The sub-transmission mechanism 61 can be, for example, a one-stage gear transmission mechanism or a continuously variable transmission mechanism.

FIG. 12 shows a schematic representation of a transmission mechanism according to FIG. 11 . In FIG. 12, the sub-transmission mechanism 61 is embodied as a second planetary gear set. Here, the second planetary gear set 61 includes at least three rotating members. In this example, a first rotating member is connected to the output 5 of the first planetary gear set 19 . In this example, a second rotating member is connected to the input of the chain/belt drive 9 . In this example, a third rotating member is connected to housing 37 (schematically shown), for example, via a first lock-up clutch or flywheel B. Here, the electric motor 33 is connected to the output 5 of the first planetary gear set 19 , for example as described with reference to FIGS. 1 to 10 . The second planetary gear set 61 may include a second lockup clutch/freewheel C between two rotating members of the second planetary gear set 61 (three possible positions shown in FIG. 12 ). Thus, using the first clutch/freewheel B and/or the second clutch/freewheel C, a selectable fixed gear ratio can be implemented with the second planetary gear set 61 . In one example, the first rotating member of the second planetary gear set 61 is a sun gear, the second rotating member of the second planetary gear set is a planet carrier, and the third rotating member of the second planetary gear set is a ring gear. / ring gear.

FIG. 13 shows a schematic representation of a transmission mechanism according to FIG. 11 . In FIG. 13, the sub-transmission mechanism 61 is embodied as a second planetary gear set. Here, the second planetary gear set 61 includes at least three rotating members. In this example, a first rotating member is connected to the output 5 of the first planetary gear set 19 . In this example, a second rotating member is connected to the input of the chain/belt drive 9 . In this example, a third rotating member is connected to housing 37 (schematically shown), for example, via a first lock-up clutch or flywheel B. Here, the second planetary gear set 61 includes a second lockup clutch/freewheel C between two rotating members of the second planetary gear set 61 (three possible positions shown in FIG. 12 ). Thus, using the first clutch/freewheel B and/or the second clutch/freewheel C, a selectable fixed gear ratio can be implemented with the second planetary gear set 61 . Here, the electric motor 33 is connected to one of the rotating members of the second planetary gear set 61 . Here, the electric motor 33 is connected to the third rotation member of the second planetary gear set 61 . In one example, the first rotating member of the second planetary gear set 61 is a sun gear, the second rotating member of the second planetary gear set is a planet carrier, and the third rotating member of the second planetary gear set is a ring gear. / ring gear.

Herein, the invention is described with reference to specific examples of embodiments of the invention. However, it will be confirmed that various modifications, variations, substitutions, and changes can be made therein without departing from the essence of the present invention.

For example, in the example of FIG. 6, the centrifugal electric motor is applied to a transmission mechanism similar to that shown in FIG. 5. It will be appreciated that a centrifugally placed electric motor could also be used in a transmission similar to that of Figures 1 to 4 or 7 to 10.

For the sake of clarity and a concise description, features are described herein as parts of the same or separate embodiments, however, alternative embodiments having combinations of all or some of the features described in these individual embodiments are also contemplated and understood to be fall within the framework of the invention as outlined in the claims. Specifications, drawings and examples should thus be regarded as an illustrative concept rather than a restrictive concept. This description is intended to embrace all alternatives, modifications, and variations that fall within the spirit and scope of the appended claims. Furthermore, many of the described elements are functional entities, which may be implemented as discrete or distributed components, or in conjunction with other components, in any suitable combination and location.

In a claim, any reference signs placed between parentheses shall not be deemed to limit the claim. Accordingly, the word "comprising" does not exclude the presence of other features or steps than those listed in a claimed item. Furthermore, "a" and its equivalents should not be construed as limited to "only one", but are used to mean "at least one", and the plural is not excluded. The sole fact that certain measures are stated in mutually distinct claims does not indicate that a combination of these measures cannot be used to produce an advantage.

1, 55, 59, 60‧‧‧transmission mechanism 1a, 1b, 59a, 59b‧‧‧transmission module 3‧‧‧crank shaft 5‧‧‧output 7‧‧‧front sprocket 9‧‧‧chain or chain Belt 11‧‧‧rear sprocket 13, 17, 35‧‧‧overrunning bearing 15‧‧‧hub 19,19'‧‧‧planetary gear set 21,23,25,21',23',25'‧‧‧ Rotating member 27‧‧‧frame 29‧‧‧torque sensor 31‧‧‧pedal 33‧‧‧electric motor 37‧‧‧cover 37a, 37b‧‧‧outer cover part 39‧‧‧stator 41‧‧‧ Rotor 41a, 41b, 53a, 53b‧‧‧part 42‧‧‧magnet 43, 45, 47, 49‧‧‧bearing 51‧‧‧spline connection 51a, 51b, 56a, 56b‧‧‧spline connection part 53 ‧‧‧coupling 54‧‧‧auxiliary member 56‧‧‧spline connection 57‧‧‧secondary transmission mechanism 61‧‧‧sub-transmission mechanism 62‧‧‧sub-transmission mechanism input 63‧‧‧sub-transmission mechanism output 64‧‧‧Second input B, C‧‧‧clutch/flywheel PC‧‧‧planet carrier R‧‧‧ring gear S, S1, S2‧‧‧sun gear p1, P2‧‧‧planetary gear pair

The invention will be further elucidated on the basis of exemplary embodiments represented in the drawings. The exemplary embodiments are provided by way of non-limiting illustration. It should be understood that the drawings are merely schematic representations of embodiments of the invention, provided by way of non-limiting examples. In the drawings: FIG. 1 shows a schematic representation of a transmission mechanism; FIG. 2 shows a simplified schematic cross-sectional view of a transmission mechanism according to FIG. 1; FIG. 3 shows a modular variant of the transmission mechanism of FIG. 1 The situation in the assembled state; Figure 4 shows the situation of the modular deformation of Figure 3 in a separate module; Figure 5 shows the situation of a modular deformation of the transmission mechanism of Figure 1 in a separate module; Figure 6 shows A simplified schematic representation of a cross-sectional view of a transmission mechanism; FIG. 7 shows a schematic representation of a transmission mechanism; FIG. 8 shows a simplified schematic representation of a transmission mechanism; FIG. 9 shows a schematic representation of FIG. 8 The situation of the transmission mechanism in a separate module; Figure 10 shows the situation that one of the transmission mechanisms of Figure 8 is deformed in a separate module; Figure 11 shows a schematic representation of a transmission mechanism; Figure 12 shows a transmission mechanism A schematic representation; and FIG. 13 shows a schematic representation of a transmission mechanism.

1‧‧‧Transmission mechanism

3‧‧‧Crankshaft

5‧‧‧Output

7‧‧‧Front sprocket

9‧‧‧chain or chain belt

11‧‧‧Rear sprocket

13, 17, 35‧‧‧Superspeed bearing

15‧‧‧Wheels

19‧‧‧planetary gear set

21, 23, 25‧‧‧Rotating member

27‧‧‧Frame

29‧‧‧Torque sensor

31‧‧‧pedal

33‧‧‧Electric motor

Claims (25)

A transmission mechanism for a bicycle, which includes: an input formed by a crankshaft, and an output connectable to a front sprocket and/or chain ring of the bicycle, connected to a frame of the bicycle A first planetary gear set connected or connected to a housing having at least three rotating members, wherein a first rotating member is connected to the crankshaft, a second rotating member is connected to the output, and a third rotating A member is connected to the housing, a sensor between the third rotating member and the housing, and a sub-actuation having a torque transfer element and having at least one sub-actuation input and a a sub-transmission output, wherein the sub-transmission input is driven by the output of the first planetary gear set and the sub-transmission output drives the front sprocket and/or chainring, wherein the sub-transmission is embodied as a first stage Type gear transmission mechanism or a stepless speed change transmission mechanism. The transmission mechanism according to claim 1, which includes an electric motor with a stator connected to the housing and a rotor connected to the output, wherein the third rotating member is formed by a planet carrier. The transmission mechanism according to claim 1, wherein at least a part of the third rotating member is part of the housing. The transmission mechanism according to claim 1, wherein one or more planet shafts are connected to the planet carrier and/or the housing. The transmission mechanism as claimed in item 1, wherein the sensor is connected to the planet carrier, and or the housing, and/or one or more of the planet shafts. The transmission mechanism according to claim 1, wherein the second rotating member is formed by a sun gear. The transmission mechanism according to claim 1, wherein the first rotating member is formed by another sun gear. The transmission mechanism according to claim 1, wherein the first rotating member is formed by a ring gear. The transmission mechanism as claimed in claim 8, wherein the planet carrier includes one or more pairs of planetary gears, wherein each pair of the planetary gears can mesh with each other, wherein one of the planetary gears of the pair of meshing planetary gears and the ring gear meshing, and one of the pair of meshing planetary gears has the other planetary gear meshing with the sun gear. The transmission mechanism of claim 1, wherein the sub-transmission mechanism is embodied as a second planetary gear set having at least three rotating members, wherein a first rotating member is connected to the output of the first planetary gear set, A second rotating member is connected to the front sprocket and/or chain ring, and a third rotating member is connected to a torque reaction force element, wherein the third rotating member of the second planetary gear set is connected to the housing There is a first clutch and/or a first flywheel therebetween, and wherein there is a second clutch and/or a second flywheel between two of the three rotating members of the second planetary gear set. Such as the transmission mechanism of claim 10, which includes a stator connected to the outer cover and an electric motor connected to a rotor connected to the output Up to, wherein the electric motor is connected to the first, second or third rotating member of the second planetary gear set. The transmission mechanism according to claim 11, wherein the electric motor is connected to the third rotating member of the second planetary gear set. The transmission mechanism according to claim 10, wherein the first rotating member of the second planetary gear set is a sun gear. The transmission mechanism according to claim 10, wherein the second rotating member of the second planetary gear set is a planet carrier. The transmission mechanism as claimed in claim 10, wherein the third rotating member of the second planetary gear set is a ring/ring gear. The transmission mechanism according to claim 2, wherein the electric motor is directly connected to the link. The transmission mechanism of claim 2, wherein an overrunning bearing or an overrunning clutch is connected between the crankshaft and the first rotating member of the first planetary gear set, and/or the output and the first planetary gear set between the second rotating member, and/or between the output and the electric motor. The transmission mechanism as claimed in claim 1, wherein the output is formed by a hollow shaft concentric with the crankshaft. The transmission mechanism according to claim 1, wherein the sensor includes one or more of a force sensor, a position sensor, a displacement sensor, and a rotation sensor. The transmission mechanism according to claim 1, which includes a calculation unit configured to calculate the torque transmitted to the housing based on a measurement value of the sensor. A bicycle, which includes a transmission mechanism according to any one of claims 1-20. A bicycle comprising the transmission mechanism according to claim 2, and comprising a control unit configured to control the electric motor according to the measured sensor value and/or the calculated torque . A method of determining a torque applied to a crankshaft of a bicycle using a sensor disposed between a third rotating member and a housing of a transmission having An input formed by the crankshaft, and an output connected to a front sprocket and/or chain ring of the bicycle, the housing is connected to a frame of the bicycle, wherein the transmission has: a first planetary gear sets, the first planetary gear set has at least three rotating members, wherein a first rotating member is connected to the crankshaft, a second rotating member is connected to the output, and the third rotating member is connected to the housing; and a sub-transmission having a torque transfer element and having at least a sub-transmission input and a sub-transmission output, wherein the sub-transmission input is driven by the output of the first planetary gear set And the sub-transmission mechanism outputs to drive the front sprocket and/or chain ring, wherein the sub-transmission mechanism is embodied as a one-stage gear transmission mechanism or a continuously variable transmission mechanism, and the method further includes: using the sensor The torque is determined on the basis of one of the measured values. The method of claim 23, wherein the sensor is Configured to measure one or more of force, position, displacement, and rotation. A method for supporting a cyclist, comprising: determining a torque applied by the cyclist to a crankshaft of a bicycle by the method according to claim 23 or 24, and controlling according to the calculated torque One of the bikes has an electric motor.

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