DE102021112219A1 - Generator module with eccentric gear for a muscle-powered vehicle and vehicle with the generator module - Google Patents

Abstract

A generator module 6 for generating electrical energy for a drive module 7 of a human-powered vehicle 1, with a generator 13 that can be driven by a vehicle user by pedaling power, the generator 13 having a rotor 17 and a stator 18, with a pedal crankshaft 12 for transmitting a pedaling power from a pedal crank 9 to the generator 13 and with a gear device 14 for transferring the pedaling force to the generator 13, with the pedal crank shaft 12 being geared to the generator 13 via the gear device 14, with the gear device 14 being designed as an eccentric gear, which has an eccentric wheel carrier 22 connected in a rotationally fixed manner to the pedal crankshaft 12 with a plurality of carrier bolts 27 as an input element, at least one eccentric wheel 23, 24 with a number of driving openings 26 and a central eccentric receiving opening 25, a ring gear section 28 and an eccentric connected in a rotationally fixed manner to the rotor 17 shaft 31 as an output element, with a carrier bolt 27 engaging in one of the driving openings 26, the eccentric shaft 31 engaging in the central eccentric receiving opening 25 and the eccentric wheel 23, 24 running in the ring gear section 28, with the carrier bolts 27 each having a contact section 40 to form a axial contact surface 41 for the at least one eccentric wheel 23, 24 have.

Description

The invention relates to a generator module for a human-powered vehicle having the features of the preamble of claim 1. The invention also relates to a vehicle having the generator module.

Electric bicycles are known which can be driven without a physical drive connection between the crank and the rear wheel. The driver uses the pedal cranks to drive a generator to generate electricity in order to supply electricity to a drive motor connected to the rear wheel. With such a drive system, the physical drive connection, such as a chain, toothed belt, cardan shaft, etc., can be omitted. In order to increase the speed of the crankshaft and reduce the torque accordingly, conventional gear types, such as single or multi-stage planetary gears, tungsten sets, etc., are usually used in order to be able to use a generator with little torque and a correspondingly small size.

The pamphlet DE 59709997 D1 discloses a vehicle that can be operated with muscle power, in particular a bicycle. The bicycle has a generator drivable by a vehicle user to generate electricity, and at least one electric motor for driving the vehicle, which is connected to the generator for transmitting electric power. In particular, between a pedal crank for driving the generator and the generator, a step-up gear is provided for a higher speed, the gear being a planetary gear, which is preferably at least partially accommodated inside the generator.

The invention is based on the object of proposing a generator module for a human-powered vehicle which is characterized by improved efficiency.

This object is achieved by a generator module having the features of claim 1 and a vehicle having the features of claim 10. Preferred or advantageous embodiments of the invention result from the dependent claims, the following description and/or the attached figures.

The subject matter of the invention is a generator module which is designed and/or suitable for generating electrical energy for a drive module of a human-powered vehicle. In particular, the vehicle is designed as an electric bicycle, also known as an e-bike. In principle, the bicycle can have exactly two wheels. Alternatively, however, the vehicle can also have more than two, in particular three or exactly four wheels.

The drive module is used to generate an electrical drive torque. The drive module preferably includes at least one electric motor, which converts electrical energy into an electrical drive torque. In this case, the drive module, in particular the electric motor, can be and/or is connected in terms of drive technology to at least or precisely one drive wheel of the vehicle. In principle, the drive module is designed as a wheel hub drive, which is integrated into the drive wheel of the vehicle. Alternatively, however, the drive module can also be arranged outside of the drive wheel and/or can serve as a central drive motor for one or more drive wheels. Basically, the drive wheel is designed as a rear wheel of the vehicle. Alternatively, however, the drive wheel can also be designed as a front wheel of the vehicle.

The generator module is in particular designed separately from the drive module. For this purpose, the generator module has a generator that can be driven by a vehicle user by pedaling. In particular, the generator generates electrical power which results from the torques and speeds applied to the generator. Preferably, the vehicle user can vary the size of the electrical power depending on the pedaling force or pedaling frequency. The drive arrangement preferably has a control device which is designed to control the drive torque and/or a drive speed of the drive module as a function of the pedaling force and/or pedaling frequency. Particularly preferably, the generator is not designed to operate as a drive motor and/or can run exclusively in generator mode. Alternatively, the generator can be operated by an electric motor, e.g. to bring the cranks into a certain position. The generator module has a stator and a rotor.

The generator module has a pedal crankshaft, which is designed and/or suitable for transmitting the pedaling force to the generator. In particular, a pedal crank is arranged at each end of the pedal crankshaft, via which the pedaling force is introduced into the pedal crankshaft. In particular, the pedal crankshaft is rotatably mounted in the generator module. The pedal crankshaft preferably defines a main axis of rotation of the generator module with its axis of rotation. The crankshaft runs continuously from one crank to the other crank.

The generator module has a transmission device which is used to translate the pedaling force is designed and/or suitable for the generator. The pedal crankshaft is connected in terms of transmission to the generator via the transmission device. In particular, the transmission device is used for stepping up (amount (i)<1), the speed at the generator being increased and the torque transmitted to the generator being reduced. The pedal crankshaft is preferably guided through the transmission device in the axial direction with respect to the main axis of rotation and/or is arranged coaxially to the transmission device. A drive train is thus formed, which leads from the crankshaft to the generator, with the crankshaft and the generator each forming part of the drive train.

In a preferred implementation, it is provided that the transmission device has a transmission ratio between the transmission input and the transmission output of less than 1:40, in particular 1:30. The transmission device preferably has a transmission ratio of between 1:10, in particular 1:30 and 1:100, in particular 1:50. The transmission device preferably has a transmission ratio of 1:50. In this way, the high pedaling torque generated by the driver (in the range of up to approx. 200Nm) at the transmission input with low speeds (in the range of 30 to 120 rpm) is converted into a lower torque with high speeds at the transmission output.

In the context of the invention, it is proposed that the gear device be designed as an eccentric gear. In particular, the eccentric gear has a gear input, in particular an input element, and a gear output, in particular an output element, with the pedal crankshaft being arranged on the input side and the generator on the output side. When driving, the pedaling torque is thus transmitted to the rotor via the eccentric gear, so that the rotor is rotated about the main axis of rotation relative to the stator. In particular, a power transmission path for transmitting the pedaling power runs from the pedal crankshaft via the eccentric gear to the generator. For this purpose, the pedal crankshaft is guided through the eccentric gear in the axial direction with respect to the main axis of rotation and/or is arranged coaxially with the eccentric gear. The eccentric gear, the pedal crankshaft and the generator are preferably arranged coaxially and/or concentrically in relation to the main axis of rotation.

According to the invention, the eccentric gear has an eccentric wheel carrier with a plurality of carrier bolts. In particular, the eccentric wheel carrier is designed as a carrier disk. The support bolts are preferably regularly distributed in the direction of rotation on a common pitch circle around the main axis of rotation. The carrier bolts preferably extend in an axial direction and/or parallel to the main axis of rotation.

According to the invention, the eccentric gear has at least or precisely one eccentric wheel with a plurality of driving openings for the carrier bolts and a central eccentric receiving opening, with each carrier bolt engaging in one of the driving openings. In particular, the free diameter of the entrainment openings is designed to be larger than the diameter of the carrier bolts.

According to the invention, the eccentric gear has a ring gear section, wherein the at least one eccentric wheel runs in operation with the outer circumference in the ring gear section. The ring gear section can be designed in one piece or in multiple pieces.

According to the invention, the eccentric gear has an eccentric shaft, the eccentric shaft engaging in the central eccentric receiving opening. In particular, the eccentric shaft has at least or exactly one eccentric section, the eccentric section having a circular cross section. The eccentric shaft preferably engages in the central eccentric receiving opening via the eccentric section. An eccentric wheel bearing device is optionally arranged between the eccentric section and the eccentric receiving opening in order to reduce friction.

According to the invention, the carrier bolts each have a contact section which is designed and/or suitable for forming an axial contact surface for the at least one eccentric wheel. In particular, the contact section has the function of guiding at least one eccentric wheel in the axial direction in relation to a bolt axis of the carrier bolt and/or holding it against axial displacement and/or tilting on the carrier bolt. During operation, the at least one eccentric wheel can preferably abut and/or run against the contact surface with its axial end face facing the contact section, so that the eccentric wheel is secured in the axial direction.

Since the run-up section rotates with the carrier bolts and thus with the eccentric wheel carrier, there is only a low relative speed between the eccentric wheel and the run-up section, which reduces the friction and thus the wear of the at least one eccentric wheel. A further advantage is that due to the axial guidance of the approach sections, only the carrier bolts themselves or the approach sections have to be manufactured precisely in order to achieve a high degree of guidance accuracy for the eccentric wheels. Thus, surrounding components, which are subordinate Exactly have performance requirements, can be manufactured more simply and cost-effectively. The high guidance accuracy that can be achieved in this way at low cost also has a positive influence on the gear noise and the gear efficiency.

In a specific embodiment, it is provided that the carrier bolts are each fixed with an axial end to the eccentric wheel carrier and have the contact section on the end facing away from the eccentric wheel carrier. In particular, the carrier bolts are positively and/or non-positively and/or firmly fixed to the eccentric wheel carrier. The eccentric wheel carrier preferably has a bolt receptacle for each carrier bolt, with the carrier bolts being held captively, in particular axially fixed, in the respective bolt receptacle. In particular, the approach section is arranged at a distance from the eccentric wheel carrier in the axial direction with respect to the bolt axis, the at least one eccentric wheel being accommodated axially between the eccentric wheel carrier and the approach section, in particular with a positive fit. A carrier bolt is thus proposed which is characterized by a simple and cost-effective design and at the same time is easy to assemble.

In a further specification, it is provided that the contact section is designed as a radially outwardly directed contact collar, with the contact surface extending at least approximately in a radial plane in relation to a bolt axis of the associated carrier bolt. In particular, “at least approximately” should be understood to mean that the contact surface extends in the radial plane, with an angular deviation of the contact surface from the radial plane of more than +/- 1 degree, preferably +/- 5 degrees, in particular +/- 10 degrees is included. The stop collar preferably has an outside diameter that is larger than an inside diameter of the entrainment openings. In particular, the stop collar is arranged coaxially and/or concentrically to the carrier bolt or the bolt axis. A carrier bolt is thus proposed which is particularly easy to manufacture.

In a first possible implementation, it is provided that the contact section and the support bolt are each formed as two separate components, with the contact section being mounted at least axially fixed on the support bolt. In principle, the carrier bolts are each designed as cylinder bolts, which are mounted accordingly in the bolt receptacle. Alternatively, however, the carrier bolts and the eccentric wheel carrier can also be made from a common material section, in particular in one piece. The approach section can be detachably or non-detachably mounted on the carrier bolt. The contact section is preferably arranged on the bolt section in a form-fitting and/or force-fitting manner and/or with a material connection in the axial direction in relation to the bolt axis. For example, the run-up section can be mounted on the carrier bolt via a screw, press or welded connection. Due to the multi-part configuration of the carrier bolt, the carrier bolt can be easily adapted to different overall widths of the eccentric gear. Furthermore, due to the multi-part configuration, the carrier bolt and the contact section can be made of different materials, for example in order to further reduce the friction on the contact surface.

In an alternative possible implementation, it is provided that the contact section and the carrier bolt are made from a common material section. In particular, the carrier bolt and the contact section are made in one piece, e.g. from a joint casting. A bolt section, which is mounted at the end with its free end in the bolt receptacle, is preferably directly adjacent to the contact section. For example, the carrier bolt can be designed as a turned part, a forged part or a formed part. A carrier bolt is thus proposed which is characterized by simple and inexpensive manufacture and a robust design.

In a further development it is provided that the eccentric gear has a bearing sleeve for each carrier bolt. In particular, the bearing sleeves serve to transmit the torque to the at least one eccentric wheel. The bearing sleeve is arranged coaxially and/or concentrically on the carrier bolt, in particular with respect to the bolt axis. The bearing sleeve is preferably designed as a non-cutting part and/or formed part. The bearing sleeve is rotatably mounted on the respective support pin via a sleeve bearing. In principle, the sleeve bearing can be designed as a plain bearing. However, the sleeve bearing is preferably designed as a rolling element bearing. The bearing sleeve is supported on the run-on section in the axial direction in relation to the bolt axis. The bearing sleeve can be arranged in the axial direction in relation to the main axis of rotation in a form-fitting manner and/or without play between the eccentric wheel carrier and on the approach section. In particular, when the sleeve bearing is designed as a rolling body bearing, the run-on section forms a rim for the rolling bodies, with the rolling bodies and/or the bearing sleeve being able to run against the run-on surface during operation. With this configuration, low-noise operation with low friction losses can be achieved in the generator module.

In a further possible embodiment it is provided that the drive arrangement has a housing which is designed and/or suitable in particular for accommodating the generator and the eccentric gear. In particular, the generator and the eccentric gear are completely accommodated in the housing. The pedal crankshaft is preferably guided in sections through the housing, with the pedal crankshaft being supported radially on the housing via at least one further bearing device, preferably a roller bearing. The housing can be constructed in several parts, preferably in two parts. In particular, the housing has a receiving space for receiving the eccentric gear and the generator, the eccentric gear and the generator being positively received in the housing in the axial and/or radial direction in relation to the main axis of rotation. The stator is preferably firmly connected to the housing.

According to this embodiment, the housing, in particular the receiving space, is divided in the axial direction with respect to the main axis of rotation by an intermediate wall into a generator space for the generator module and a gear space for the gear module. In particular, the gear compartment can be configured as a wet compartment, in particular provided with oil or grease lubrication, and the generator compartment can be configured as a dry compartment. The intermediate wall is preferably supported in the radial direction on the housing on the one hand and on the eccentric shaft on the other hand, preferably in a fluid-tight manner. In particular, the intermediate wall can be in sealing contact with the eccentric shaft and/or the housing via a seal. Alternatively or optionally in addition, the intermediate wall can be permanently connected to the housing. It is provided that the intermediate wall is arranged at a distance from the at least one eccentric wheel in the axial direction. In particular, the partition wall does not assume any guiding function for the at least one eccentric wheel, so that the partition wall can be manufactured particularly easily and inexpensively. If the generator space does not have to be sealed off from the gear space, the partition wall can also be dispensed with entirely according to the invention, with the guide function of the at least one eccentric wheel being taken over exclusively by the carrier bolts or the contact sections. As a result, the drive arrangement can be made more compact and less expensive.

In a further specific implementation, it is provided that the eccentric gear has two eccentric wheels that are offset diametrically and/or in opposite directions, e.g. by 180° in the direction of rotation. The eccentric wheels are preferably arranged axially adjacent to one another. The eccentric wheels are preferably arranged in contact with one another and/or slide off one another during operation. The two eccentric wheels are arranged in the axial direction between the eccentric wheel carrier and the approach section. Preferably, the two eccentric wheels are arranged in a form-fitting manner in the axial direction in relation to the bolt axis or with a small axial play between the eccentric wheel carrier and the approach section. This implementation reduces transverse forces in the eccentric gear.

In a first possible implementation, the at least one, preferably both, eccentric wheels can be designed as cam discs. In particular, the cam disk is designed as a flat disk which has a curved shape on the outer circumference. The curve shape of the at least one cam disc and the inner contour of the ring gear section can in principle be of any desired design, as long as they can assume the function of the eccentric gear. However, the eccentric gear is particularly preferably designed as a cycloid gear, with a cycloid shape being represented by the outer circumference of the at least one cam disk.

In a second possible implementation, the at least one, preferably both, eccentric wheels can be designed as toothed wheel disks. In particular, the gear wheel disk is designed as a flat disk. The toothed wheel disk has external teeth on the outer circumference and the ring gear section has internal teeth on the inner circumference, the outer teeth being in engagement with the inner teeth in some areas. The respective toothing is designed in particular as an involute toothing. Particularly preferably, the number of teeth of the inner circumferential spur gear and the outer circumferential spur gear differ by at least or exactly one tooth.

In one possible implementation, it is provided that the eccentric wheel carrier forms an input element of the transmission device and the eccentric shaft forms an output element of the transmission device. In particular, the eccentric wheel carrier is connected to the pedal crankshaft in a rotationally fixed manner for this purpose, and the eccentric shaft is connected in a rotationally fixed manner to the rotor. The ring gear section is fixed or at least non-rotatably connected to the housing. Alternatively, the ring gear section forms the input element of the transmission device and the eccentric shaft forms the output element of the transmission device. In particular, the ring gear section is non-rotatably connected to the pedal crankshaft and the eccentric shaft is non-rotatably connected to the rotor. The eccentric wheel carrier is connected to the housing in a fixed or at least non-rotatable manner. In particular, the input organ positively and/or non-positively and/or cohesively with the pedal crankshaft, preferably at least non-rotatably connected. Alternatively, the input element and the pedal crankshaft can also be formed from a common material section. In particular, the output member is connected to the rotor in a form-fitting and/or force-fitting and/or cohesive manner, preferably at least in a rotationally fixed manner. Alternatively, the output member and the rotor can also be formed from a common material section. The input element is preferably arranged coaxially and/or concentrically with respect to the main axis of rotation with respect to the pedal crankshaft and/or the output element is arranged coaxially and/or concentrically with respect to the main axis of rotation with respect to the rotor.

A further object of the invention relates to a drive arrangement with the generator module and the drive module, as these have already been described above. In order to provide the electrical energy, the generator module is connected directly to the drive module via an electrical line. In particular, the electric motor can thus be fed directly by the current generated by the generator. Alternatively or optionally in addition, the generator module is connected to the drive module indirectly via an energy storage module to provide the electrical energy. In particular, the energy storage module is designed as an accumulator, which is fed by the generator while driving and can also be charged from an external power source. In particular, the electric motor can thus be fed by the current stored in the energy storage module.

Another subject matter of the invention relates to a vehicle with the generator module and/or the drive arrangement as already described above.

In particular, the vehicle is a human-powered vehicle, in particular a bicycle, which is driven by an electric motor. In particular, the vehicle is characterized in that the electrical energy required for the electric motor is at least partially generated by the driver using the generator module.

• 1 eine schematische Darstellung eines Fahrzeugs mit einer Antriebsanordnung als ein Ausführungsbeispiel der Erfindung;
• 2 eine Schnittdarstellung eines Generatormoduls der Antriebsanordnung.

Further features, advantages and effects of the invention result from the following description of a preferred exemplary embodiment of the invention and the attached figures. show:

• 1 a schematic representation of a vehicle with a drive arrangement as an embodiment of the invention;
• 2 a sectional view of a generator module of the drive arrangement.

Corresponding or identical parts are each provided with the same reference symbols in the figures.

1 shows a muscle-powered vehicle 1 in a highly simplified representation. The vehicle 1 is designed as a bicycle, which is essentially formed from a frame 2 and a front wheel 3 and a rear wheel 4 .

The vehicle 1 has a drive arrangement 5 which is used to drive the rear wheel 4 . The rear wheel 4 thus forms a drive wheel of the vehicle 1, with the front wheel 3 remaining unpowered. Optionally, however, it can also be provided that the front wheel 3 is driven.

The drive arrangement 5 includes a generator module 6, optionally a drive module 7 and an energy storage module 8. The generator module 6 is arranged in the area of the bottom bracket and can be driven by a vehicle user by pedaling power in order to generate electrical energy for the drive module 7. For this purpose, the generator module 6 has two pedal cranks 9 arranged diametrically opposite one another, which are set in rotation by pedaling force in order to generate electrical power in the generator module 6 .

The bicycle has no mechanical drive connection between the pedal cranks 9 and the drive wheel 4 . The generator module 6 is only electrically connected to the drive module 6 and/or the energy storage module 8 via an electrical line 10 in order to provide the electrical energy required for the drive module 7 . The drive module 7 can be designed, for example, as a wheel hub motor that is integrated into the rear wheel 4 and transmits an electrical drive torque to the rear wheel 4 . The drive module 7 can be supplied directly by the electrical energy generated by the generator module 6 or indirectly by the electrical energy stored in the energy storage module 8 . The energy storage module 8 can be fed by the generator module 6 while driving and can also be charged from an external power source. Optionally, the electrical energy provided by the generator module 6 can be made available to a consumer 11, e.g. light.

the 2 shows the generator module 6 in a longitudinal section along a main axis of rotation 100. The generator module 6 has a pedal crankshaft 12, which defines the main axis of rotation 100 with its axis of rotation. In a built-in situation tion, the cranks 9 are mounted on the end of the crankshaft 12 .

The generator module 6 has a generator 13 and a transmission device 14 which are accommodated together in a housing 15 . The generator 13 has a stator 16 and a rotor 17 , with the pedal crankshaft 12 being connected to a transmission input and the rotor 17 being connected to a transmission output of the transmission device 14 . The stator 16, on the other hand, is fixed to the housing 15 and thus remains stationary. The transmission device 14 serves to convert a pedaling torque introduced into the pedal crankshaft 12 to the generator 13 via the transmission device 14 .

The gear device 14 is designed as an eccentric gear. The eccentric gear 14 is arranged in relation to the main axis of rotation 100 coaxially to the generator 13 and the pedal crankshaft 12 and in the axial direction with a positive fit between the generator 13 and the housing 15 .

The housing 15 is designed in two parts, with the housing 15 having a housing base body 18 which is closed off in the axial direction by a housing cover 19 . The housing base body 18 and the housing cover 19 each have a central passage opening 20 , 21 which is used to guide the pedal crankshaft 12 through the housing 15 .

The eccentric gear 15 has an eccentric wheel carrier 22 as an input element, which is connected to the pedal crankshaft 12 in a rotationally fixed manner. The eccentric wheel carrier 22 is designed in one piece with a shaft extension of the pedal crankshaft 12 so that a shaft-hub connection between the pedal crankshaft 12 and the transmission device 14 can be saved. When the pedal crankshaft 12 rotates, the eccentric wheel carrier 22 is also rotated and the rotational movement is accelerated. In a preferred implementation, it is provided that the eccentric gear 14 has a transmission ratio between the gear input and the gear output with an amount of less than 1:30. The eccentric gear 14 preferably has a transmission ratio of between 1:30 and 1:100. The eccentric gear 14 preferably has a transmission ratio of 1:50. In this way, the high pedaling torque generated by the driver (in the range of up to approx. 200 Nm) at the transmission input/input element at low speeds (in the range from 30 to 120 rpm) is converted into a lower torque with high speeds at the transmission output/output element.

Furthermore, two eccentric wheels 23, 24 are provided, the eccentric wheels 23, 24 each having an eccentric receiving opening 25 and a plurality of eccentric driving openings 26. The eccentric wheels 23, 24 are arranged opposite to each other in order to reduce lateral forces during operation.

The eccentric wheel carrier 22 has a plurality of carrier bolts 27, the carrier bolts 27 engaging in the driving openings 26 of the eccentric wheels 23, 24, so that they are carried along in the direction of rotation by the carrier bolts 27 and thus by the eccentric wheel carrier 22. For this purpose, the carrier bolts 27 are fixed to the eccentric wheel carrier 22 and extend in the axial direction with respect to the main axis of rotation 100 radially inside a ring gear section 28 which is connected to the housing base body 18 in a torque-proof manner.

The eccentric gears 23, 24 have external teeth 29 on their outer circumference and the ring gear section 28 has internal teeth 30 on its inner circumference, with the external teeth 29 and the internal teeth 30 only intermeshing in sections and offset by 180° and/or in opposite directions. For example, the external toothing 29 and the internal toothing 30 are designed as spur gearing, in particular as involute gearing.

An output element of the eccentric gear 14 is designed as a hollow shaft 31, the hollow shaft 31 having two eccentric sections 32, 33, the eccentric sections 32, 33 engaging in the eccentric receiving opening 25 of the eccentric wheels 23, 24 via an eccentric wheel bearing device 34 in each case. The hollow shaft 31 is connected to the rotor 17 in a torque-proof manner. The crankshaft 12 is arranged coaxially to the hollow shaft 31 with respect to the main axis of rotation 100, wherein the crankshaft 12 is mounted relative to the hollow shaft 31 and/or to the rotor 17 via a rotor bearing device 35 and is designed, for example, as a rolling element bearing.

The gear module 6 has an intermediate wall 36 which divides the housing 15 into a generator space 37 for accommodating the generator 13 and a gear space 38 for accommodating the gear mechanism 14 , in particular the eccentric gear 14 . In order to further reduce the friction losses in the generator module 6, in particular in the gear mechanism 14 and in particular in the eccentric gear 14, the gear chamber 38 is provided with oil or grease lubrication. The generator space 37 preferably forms a dry space, with the gear space 38 being separated from the dry space by the intermediate wall 36 and a sealing device 39 relative to the hollow shaft 31 . For example, the sealing device Device 39 is designed as a radial shaft sealing ring which rests sealingly on an outer circumference of the hollow shaft 33 .

The eccentric wheel 24 facing away from the eccentric wheel carrier 22 must be guided axially or held against axial displacement and tilting. If this is done conventionally through the intermediate wall 36, the high relative speed between the pedal crankshaft 12 and the housing 15 creates additional friction, which impairs the overall efficiency of the generator module 6. In addition, very precise guidance is required between this eccentric wheel 24 and the intermediate wall 36, so that high demands are placed on the precision of the individual parts involved, and high component costs are thus incurred.

In order to optimize both the efficiency and to keep the component costs low, it is proposed to provide the carrier bolts 27 with a contact section 40 which forms a contact surface 41 in the axial direction in relation to the main axis of rotation 100 for the eccentric wheel 24 . The contact section 40 is designed as a contact collar, which adjoins the respective carrier bolt 27 in the radial direction in relation to a bolt axis 101 on the side facing away from the eccentric wheel carrier 27 . The contact surface 41 extends in a radial plane in relation to the pin axis 101, the eccentric wheel 24 being guided or held axially on the contact surface 41. The approach sections 40 each have a radial extent that is greater than a maximum diameter of the entrainment openings 26.

In this exemplary embodiment, the carrier bolts 27 and the respectively associated contact section 40 are made from a common material section. For example, the support bolts 27 and the contact sections 40 are made in one piece, e.g. from a single cast. The free axial end of the carrier bolt 27 is captively mounted in a corresponding bolt receptacle 42 of the eccentric wheel carrier 22, e.g. via a press connection.

It can also be seen that a bearing sleeve 43 is placed on the carrier bolt 27 coaxially to the bolt axis 101 and is secured axially by the contact section 40 or is supported axially on the contact surface 41 . The bearing sleeve 43 is rotatably mounted on the carrier pin 27 via a sleeve bearing 44 . The sleeve bearing 44 is designed as a sliding bearing or as a rolling element bearing. The outer diameter of the support bolts 27 is smaller than the entrainment openings 26 so that the bearing sleeves 43 can run off the inner circumference of the entrainment openings 26 . Designed as a rolling body bearing, the sleeve bearing 44 has a plurality of rolling bodies distributed around the bolt axis 101, with the approach section 40 forming a lateral rim for the rolling bodies.

Since the run-up section 40 rotates with the eccentric wheel carrier 22, the lower relative speed between the run-up section 40 and the eccentric wheels 23, 24 results in less friction, which leads to increased efficiency and less wear. A further advantage is that only the carrier bolts 27 have to be manufactured precisely in order to achieve a high level of guiding accuracy for the eccentric wheels 23, 24. As a result, the housing 15 and the intermediate wall 36 can be manufactured much more simply and cost-effectively, since these components only have subordinate accuracy requirements and are no longer used to guide the eccentric gears 23, 24. The high guiding accuracy that can be achieved in this way at low cost also has a positive influence on the gear noise and the other gear efficiency of the gear device 14. If the generator space 37 within the housing 15 does not have to be sealed off from the gear space 38, the intermediate wall 36 can also be dispensed with completely, since the guiding function is taken over exclusively by the carrier bolts 27. This saves installation space and reduces costs.

Reference List

1

vehicle

2

frame

3

front wheel

4

rear wheel

5

drive assembly

6

generator module

7

drive module

8th

energy storage module

9

crank

10

Management

11

consumer

12

pedal crankshaft

13

generator

14

gear mechanism

15

Housing

16

stator

17

rotor

18

housing body

19

housing cover

20

passage opening

21

passage opening

22

eccentric wheel carrier

23

first eccentric wheel

24

second eccentric wheel

25

eccentric receiving opening

26

entrainment openings

27

support bolts

28

ring gear section

29

external teeth

30

internal teeth

31

hollow shaft

32

first eccentric section

33

second eccentric section

34

eccentric wheel bearing device

35

rotor bearing device

36

partition

37

generator room

38

gear room

39

sealing device

40

approach section

41

contact surface

42

bolt mount

43

bearing sleeve

44

sleeve storage

100

main axis of rotation

101

bolt axle

QUOTES INCLUDED IN DESCRIPTION

This list of the documents cited by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent Literature Cited

• DE 59709997 D1 [0003]

Claims (10)

Generator module (6) for generating electrical energy for a drive module (7) of a human-powered vehicle (1), with a generator (13) that can be driven by a vehicle user by pedaling power, with a pedal crankshaft (12) for transmitting pedaling power from a pedal crank (9) to the generator (13), with a gear device (14) for transferring the pedaling force to the generator (13), the pedal crankshaft (12) being geared to the generator (13) via the gear device (14), characterized in that the gear device (14) is designed as an eccentric gear which has an eccentric wheel carrier (22) with several carrier bolts (27), at least one eccentric wheel (23, 24) with several driving openings (26) and a central eccentric receiving opening (25), a ring gear section (28 ) and an eccentric shaft (31), wherein a support bolt (27) engages in one of the driving openings (26), the eccentric shaft (31) in the center e engages in the eccentric receiving opening (25) and the eccentric wheel (23, 24) runs in the ring gear section (28), the carrier bolts (27) each having a contact section (40) to form an axial contact surface (41) for the at least one eccentric wheel (23, 24). Generator module (6) after claim 1 , characterized in that the carrier bolts (27) are each fixed with an axial end on the eccentric wheel carrier (22) and on the eccentric wheel carrier (22) facing away from the stop section (40). Generator module (6) after claim 1 or 2 , characterized in that the contact section (40) is designed as a radially outwardly directed contact collar, the contact surface (41) in relation to a bolt axis (101) of the associated carrier bolt (27) extending at least approximately in a radial plane. Generator module (6) according to one of the preceding claims, characterized in that the contact section (40) and the support bolt (27) are each designed as separate components, the contact section (40) being mounted at least axially fixed on the support bolt (27). Generator module (6) according to one of Claims 1 until 3 , characterized in that the stop section (40) and the support bolt (27) are made of a common material section. Generator module (6) according to one of the preceding claims, characterized in that the eccentric gear (14) has a bearing sleeve (43) for each support bolt (27), the bearing sleeve (43) being rotatable on the respective support bolt (27) via a sleeve bearing (44). ) is mounted, wherein the bearing sleeve (43) is supported in the axial direction with respect to a bolt axis (101) on the stop section (40). Generator module (6) according to one of the preceding claims, characterized by a housing (15), wherein the housing (15) in the axial direction with respect to a main axis of rotation (100) through an intermediate wall (36) into a generator space (37) for the generator (13) and a gear space (38) for the gear device (14), the intermediate wall (36) being arranged at a distance from the at least one eccentric wheel (23, 24) in the axial direction. Generator module (6) according to one of the preceding claims, characterized in that the eccentric gear (14) has two diametrically and/or oppositely offset eccentric wheels (23, 24), the two eccentric wheels (23, 24) being located in the axial direction between the eccentric wheel carrier ( 22) and the approach section (40) are held in a form-fitting manner. Generator module (6) according to one of the preceding claims, characterized in that the eccentric wheel carrier (22) or the hollow wheel section (28) forms an input element of the transmission device (14) and the eccentric shaft (31) forms an output element of the transmission device (14). Vehicle (1) with the generator module (6) according to one of the preceding claims.

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