阅读说明：本技术 用于自行车或电动自行车的驱动机构 (Drive mechanism for a bicycle or electric bicycle ) 是由 J·卡尔滕巴赫 U·格里斯迈尔 于 2019-08-12 设计创作，主要内容包括：提出一种用于自行车或电动自行车的驱动机构,驱动机构具有：在壳体中的人力驱动轴(1)、第一电驱动装置(EM 1)的与人力驱动轴(1)以轴线平行的方式布置的转子(3)、以及第二电驱动装置(EM 2)的与人力驱动轴(1)共轴地布置的转子(4),其中第一电驱动装置(EM 1)的转子(3)藉由第一固定传动装置与作为叠加传动装置的第一行星齿轮组(PS 1)联接,其中第二电驱动装置(EM 2)的转子(4)藉由第二固定传动装置与人力驱动轴(1)联接,其中人力驱动轴(1)与作为叠加传动装置的第一行星齿轮组(PS 1)联接,并且其中作为叠加传动装置的第一行星齿轮组(PS 1)与从动装置(5)联接。(A drive mechanism for a bicycle or an electric bicycle is proposed, the drive mechanism having: a manual drive shaft (1) in the housing, a rotor (3) of the first electric drive (EM 1) arranged in an axially parallel manner to the manual drive shaft (1), and a rotor (4) of the second electric drive (EM2) arranged coaxially to the manual drive shaft (1), wherein the rotor (3) of the first electric drive (EM 1) is coupled to the first planetary gear set (PS 1) as a superposition gear by means of a first fixed gear, wherein the rotor (4) of the second electric drive (EM2) is coupled to the manual drive shaft (1) by means of a second fixed transmission, wherein the manual drive shaft (1) is coupled to a first planetary gear set (PS 1) as a superposition transmission, and wherein the first planetary gear set (PS 1) as a superposition gear is coupled to the output (5).)

1. A drive mechanism for a bicycle or electric bicycle, the drive mechanism having: a manual drive shaft (1) in a housing (2), a rotor (3) of a first electric drive (EM 1) arranged in an axis-parallel manner to the manual drive shaft (1), and a rotor (4) of a second electric drive (EM2) arranged coaxially to the manual drive shaft (1), wherein the rotor (3) of the first electric drive (EM 1) is coupled to the first planetary gear set (PS 1) as a superposition gear by means of a first fixed gear, wherein the rotor (4) of the second electric drive (EM2) is coupled to the manual drive shaft (1) by a second stationary transmission, wherein the manual drive shaft (1) is coupled to the first planetary gear set (PS 1) as a superposition gearing, and wherein the first planetary gear set (PS 1) as a superposition gear is coupled to the output (5).

2. The drive mechanism according to claim 1, characterized in that said first electric drive means (EM 1) is dimensioned larger than said second electric drive means (EM 2).

3. Drive mechanism according to claim 1 or 2, characterized in that a single-stage or multi-stage spur gear transmission is provided as the first fixed transmission.

4. A drive mechanism according to claim 1 or 2, characterized in that a third planetary gear set (PS 3) is provided as the first stationary transmission.

5. Drive mechanism according to one of the preceding claims, characterized in that the first fixed transmission is coupled to the first planetary gear set (PS 1) as a superposition transmission by means of an intermediate gear (Z6) or a chain or belt transmission (10).

6. Drive mechanism according to one of the preceding claims, characterized in that a harmonic drive (WG) is provided as second stationary drive.

7. The drive mechanism according to claim 6, characterized in that the wave generator (6) of the harmonic drive (WG) is connected to the rotor (4) of the second electric drive (EM 2); a deformable inner sleeve (7) with an outer toothing of the harmonic drive (WG) is connected to the manual drive shaft (1); and an outer sleeve (8) with the inner toothing of the harmonic drive (WG) is fixed to the housing.

8. Drive mechanism according to one of claims 1 to 5, characterized in that a second planetary gear set (PS 2) is provided as second fixed transmission.

9. The drive mechanism according to claim 8, characterized in that the second planetary gear set (PS 2) is embodied with multi-stage planetary gears.

10. The drive mechanism according to one of the preceding claims, characterized in that the first stationary transmission is connected with the sun gear (11) of the first planetary transmission (PS 1) as a superposition transmission; the manual drive shaft (1) is connected to the planet carrier (12) of the first planetary gear set (PS 1) as a superposition gear and the output (5) is connected to the ring gear (13) of the first planetary gear set as a superposition gear; or the manual drive shaft (1) is connected to the ring gear (13) of the first planetary gear set (PS 1) as a superposition gear and the output (5) is connected to the planet carrier (12) of the first planetary gear set as a superposition gear.

11. Drive mechanism according to one of the preceding claims, characterized in that the manual drive shaft (1) is embodied as a pedal bearing crankshaft and the housing (2) is embodied as a pedal bearing housing.

12. The drive mechanism according to one of the preceding claims, characterized in that the driven means (5) is embodied as a sprocket or a pulley.

13. Drive mechanism according to one of the preceding claims, characterized in that the first electric drive (EM 1) and the second electric drive (EM2) are embodied as electric machines which can be driven both as an engine and as a generator, respectively.

14. Bicycle or electric bicycle having a drive mechanism according to one of the preceding claims.

Technical Field

The present invention relates to a drive mechanism for a motor-assisted bicycle or electric bicycle, having a manual drive shaft in a housing, and a first, larger-sized electric drive and a second, smaller-sized electric drive. The invention also relates to a motor-assisted bicycle or electric bicycle with a drive mechanism.

Background

A drive mechanism for an electric bicycle is known, for example from document WO 2016/034574, in which a first electric drive of larger dimensions and a second electric drive of smaller dimensions are provided. The larger drive means is arranged coaxially with the pedal bearing crankshaft, while the smaller drive means is arranged in an axis-parallel manner with the pedal bearing crankshaft. As a superposition gear, a planetary gear is provided which requires a large installation space, since the superposition gear has to be designed with a large transmission ratio. The first drive is directly connected to the sun gear of the planetary gear. Since the sun gear passes through the pedal bearing crankshaft, a minimum sun gear diameter is required. In order to support the sun gear of the planetary gear unit, which is designed to be relatively large, a correspondingly large-sized first drive is also required in order to achieve the required support torque for the pedal force of the driver and possibly the assistance torque for the second electric drive. The disadvantage is that the installation space requirement in the axial direction and in the radial direction is large in the case of the known drive mechanism.

Disclosure of Invention

The basic object of the present invention is to provide a drive mechanism and a bicycle or electric bicycle of the type mentioned in the introduction, by means of which a superimposed function can be achieved with the least possible requirement for installation space.

This object is achieved according to the invention by the features of patent claims 1 or 14, wherein advantageous and claimed improvements result from the subclaims and the description and the drawing.

Accordingly, a drive train for an engine-assisted bicycle or electric bicycle is proposed, which has a manual drive shaft in a housing. In order to provide a mechanism optimized in terms of structural form, the following is proposed: a rotor of a first electric drive, which is arranged axially parallel to a manual drive shaft, and a rotor of a second electric drive, which is arranged coaxially to the manual drive shaft, are provided, wherein the rotor of the first electric drive is coupled to a first planetary gear set as a superposition transmission by means of a first fixed transmission, wherein the rotor of the second electric drive is coupled to the manual drive shaft by means of a second fixed transmission, wherein the manual drive shaft is coupled or connected to the first planetary gear set as a superposition transmission, and wherein the first planetary gear set as a superposition transmission is coupled or connected to a driven device.

The proposed connection and arrangement based on the electric drive and the further transmission component provides a drive mechanism which is optimized with respect to installation space in comparison with known drive mechanisms.

A development of the invention may provide that the first electric drive is dimensioned larger than the second electric drive. Thus, the first electric drive is dimensioned larger, while the second electric drive is dimensioned smaller. The drive mechanism, which is particularly space-optimized, is provided by the following means, namely: of these two drives, the larger or the larger-sized electric drive, which can change the pedal frequency, is arranged in an axially parallel manner, while the smaller or the smaller-sized drive, which is firmly connected to the manual drive shaft, is arranged coaxially to the latter. The following advantages are thereby obtained: the installation space required in the region of the manual drive shaft is small, since the second electric drive, which is smaller in size, is arranged there. Since the larger electric drive is arranged in an axially parallel manner, a larger installation space is created in the axial direction on this axis, since in the larger first drive only the first fixed gear is arranged in this region.

The superposition transmission provides a superposition function which enables a speed variability in that the pedal frequency can be varied by changing the speed of the first electric drive at a given driving speed by means of the superposition function of the superposition transmission. For this reason, no conventional mechanical transmission is required. Thus, a CVT transmission is realized to some extent by means of the drive mechanism according to the invention, so that conventional mechanical transmission adjustment devices, such as chain shifters or hub shifters, are not required. The term "CVT" generally refers to a continuously variable transmission.

Within the scope of the development of the invention, it can be provided that a single-stage or multi-stage spur gear is provided as the first fixed gear for the first electric drive. The term "fixed transmission" is to be understood by a person skilled in the art as a transmission ratio having a constant transmission value. The spur gear can be in the form of a countershaft design, for example, i.e., it can be embodied with a countershaft. Instead of a spur gear, however, an additional planetary gear or a planetary gear set can also be provided. The spur gear or planetary gear set can be connected to the superposition gear, for example, by a chain or belt drive or also by an intermediate gear, so that the drive output of the first electric drive acts at a constant transmission ratio on the superposition gear.

A further embodiment of the invention can provide that a harmonic drive or the like is provided as the second fixed drive. The harmonic drive can be compared in its function to a simple positive planetary gear set. The elements of the harmonic drive are fixed to the housing such that the constant gear ratio of the second drive acts on the manual drive shaft. Instead of a harmonic drive, a planetary drive or a planetary gear set 1 can also be provided as a second fixed drive for the second electric drive. Independently of the respective embodiment, the second fixed transmission acts on a manual drive shaft, which is then connected to the superposition transmission.

Independently of the respective embodiment of the invention, proposed in the drive mechanism are: the first fixed gear is connected directly or indirectly to the sun gear of the first planetary gear as a superposition gear. The respective drive power of the first electric drive is thus transmitted to the superposition transmission with a constant transmission ratio. The manual drive shaft is connected directly or indirectly to the planet carrier and the output of the drive mechanism is connected directly or indirectly to the ring gear of the superposition transmission, or the manual drive shaft is connected directly or indirectly to the ring gear and the output is connected directly or indirectly to the planet carrier of the conversion transmission.

A particularly advantageous embodiment of the invention is achieved in that: the manual drive shaft is implemented as a pedal bearing crankshaft and the housing is implemented as a pedal bearing housing. Therefore, the proposed drive mechanism is disposed as a center motor in a pedal bearing housing of an electric bicycle.

Another aspect of the invention is to claim an engine-assisted bicycle or electric bicycle having the above-described drive mechanism. Accordingly, an electric bicycle is presented having an electric CVT with an input-coupled electric drive coaxial with a pedal-bearing crankshaft. The advantages already described and further advantages result here.

Drawings

The invention is further elucidated below with the aid of the drawing. In the drawings:

fig. 1 shows a schematic view of a first embodiment variant of the drive mechanism according to the invention;

fig. 2 shows a schematic side view of a first embodiment variant according to fig. 1;

fig. 3 shows a schematic view of a second embodiment variant of the drive mechanism;

fig. 4 shows a schematic view of a third embodiment variant of the drive mechanism;

fig. 5 shows a schematic side view of a third embodiment variant according to fig. 4;

fig. 6 shows a schematic view of a fourth embodiment variant of the drive mechanism;

fig. 7 shows a schematic view of a fifth embodiment variant of the drive mechanism;

fig. 8 shows a schematic view of a sixth embodiment variant of the drive mechanism; and is

Fig. 9 shows a schematic view of a seventh embodiment variant of the drive mechanism.

Detailed Description

Fig. 1 to 9 show, by way of example only, different embodiment variants of the drive mechanism for bicycles or electric bicycles according to the invention and therefore do not limit the different structural alternatives described and claimed above.

The drive mechanism comprises a manual drive shaft 1 in a housing 2, wherein the drive shaft 1 is embodied as a pedal bearing crankshaft in the illustrated embodiment variant and is arranged in a pedal bearing housing as the housing 2. In this connection, the term "human powered drive shaft 1" means that the human powered drive shaft is a drive shaft that can be driven or operated by human power. Thus, a kick crankshaft (i.e., a crankshaft that is stepped on by a foot) is an exemplary embodiment of human powered drive shaft 1.

The drive mechanism includes: for example, a rotor 3 of the first, larger electric drive EM 1, which is arranged axially parallel to the manual drive shaft 1, and a rotor 4 of the second, smaller electric drive EM2, which is arranged coaxially to the manual drive shaft 1. In this connection, the expression "larger" means that the size is set larger and the expression "smaller" means that the size is set smaller. Thus, first electric drive EM 1 has a higher power and/or a larger size than second electric drive EM 2. The first electric drive EM 1 and the second electric drive EM2 are each preferably designed as an electric machine which can be used both as an engine and as a generator.

Furthermore, in the proposed drive, it is proposed that the rotor 3 of the first electric drive EM 1 is coupled via a first fixed transmission to the first planetary gear set PS 1 as a superposition transmission. The rotor 4 of the second electric drive EM2 is coupled to the manual drive shaft by a second stationary transmission. Thus, the second electric drive EM2 is input coupled to the pedal bearing crankshaft or the manual drive shaft 1 by means of a second stationary transmission. The manual drive shaft 1 is connected to a first planetary gear set PS 1 as a superposition transmission, wherein the first planetary gear set PS 1 as a superposition transmission is connected to the output of the drive train 5. The driven device 5 can preferably be embodied as a sprocket or pulley of a bicycle or electric bicycle and is arranged outside or inside the housing 2. The first planetary gear set PS 1 as a superposition gear is therefore arranged coaxially with the pedal bearing crankshaft or the manual drive shaft 1.

Fig. 1 shows an exemplary first embodiment variant of the drive, in which a 2-stage spur gear is assigned to the first electric drive EM 1 as a first fixed gear. The rotor 3 of the first electric drive EM 1 is connected to the first gear Z2 of the first stage of the spur gear. The first gear wheel Z2 is in engagement with the second gear wheel Z3 of the first stage of the spur gear arrangement and is connected in a rotationally fixed manner with the countershaft 9. The first gear wheel Z4 of the second stage of the spur gear is likewise connected in a rotationally fixed manner to the countershaft 9 and is coupled via a belt or chain drive 10 to a second gear wheel Z1 of the second stage of the spur gear, which is connected to the sun gear wheel 11 of the first planetary gear set PS 1 as a superposition gear. The planet carrier 12 of the first planetary gear set PS 1 is connected to the manual drive shaft 1. The ring gear 13 of the first planetary gear set PS 1 is connected to the driven device 5.

The harmonic drive WG is assigned to the second electric drive EM2 as a second fixed drive. The harmonic drive WG is also referred to as a stress harmonic drive or sliding key drive, among others. The harmonic drive WG has a wave generator 6, an inner sleeve 7 and an outer sleeve 8. The outer sleeve 8 has an internal toothing and the inner sleeve 7 has an external toothing, which are in engagement with one another by means of, for example, two circumferential segments. The cross-section of the outer sleeve 8 is circular. The inner sleeve 7 is designed to be deformable. By means of the wave generator 6 having an elongated or oval shape, the inner sleeve 7 is pressed with its outer teeth into the inner teeth of the outer sleeve 8 by means of, for example, two circumferential sections. The number of teeth of the external teeth of the inner sleeve 7 and the number of teeth of the internal teeth of the outer sleeve 8 are different from each other.

The wave generator 6 of the harmonic drive WG is connected to the rotor 4 of the second electric drive EM2 and forms the drive, as seen from the second electric drive EM 2. A deformable inner sleeve 7 with the outer toothing of the harmonic drive WG is connected to the manual drive shaft 1 and forms the output from the perspective of the second electric drive EM 2. An outer sleeve 8 with the inner toothing of the harmonic drive WG is fixed to the housing. The harmonic drive WG therefore serves as a second stationary drive for the second electric drive EM 2.

Thus, the second, smaller electric drive EM2 is arranged coaxially with the pedal bearing crankshaft or the manual drive shaft 1. The harmonic drive WG is used only as a second stationary drive of the second electric drive EM2 to the manual drive shaft 1. The following advantages are thereby obtained: the harmonic drive WG is loaded only by the second electric drive EM2 and not by the pedal force of the driver. The harmonic drive WG can therefore be dimensioned correspondingly smaller and a higher transmission ratio can be achieved with advantageously smaller installation space requirements. Furthermore, the manual drive shaft 1 is connected to the first planetary gear set PS 1 as a superposition transmission, for example by means of a planet carrier or planet carrier 12. Driven by the ring gear 13 of the first planetary gear set PS 1. The sun gear 11 of the first planetary gear set PS 1 is connected to the first electric drive EM 1 by means of a 2-stage spur gear transmission. The following advantages are obtained in comparison with known drive mechanisms: at the sun gear 11, the pedal-bearing crankshaft or the manual drive shaft 1 only has to support a small torque, since the manual drive shaft 1 is connected to the planet gear carrier 12. The first, larger electric drive EM 1 is arranged in an axially parallel manner and is connected to the sun gear 11 of the first planetary gear set PS 1 by means of a 2-stage spur gear as a first fixed gear, whereby the following advantages result: thus, a larger first electric drive EM 1 is provided with more axial installation space than a smaller second electric drive EM 2.

As high a fixed transmission ratio as for the second electric drive EM2 cannot be achieved for the first electric drive EM 1, since the first electric drive EM 1 must cover a higher rotational speed range than the second electric drive EM 2. The pedal frequency is varied by the rotational speed of the first electric drive EM 1 at different driving speeds. The second electric drive EM2 always rotates at the same rate as the manual drive shaft 1, whose rotational speed is limited by the possible pedal crank rotational speed that can be achieved by the driver. Therefore, the 2-stage spur gear transmission is sufficient as a first fixed transmission for the first electric drive EM 1. The first electric drive EM 1 requires a greater torque than the second electric drive EM2, which may be achieved, for example, by a greater length of the electric machine. In the example illustrated, the 2-stage spur gear for the first drive EM 1 is formed by a first gear pair Z2/Z3 and a second gear pair Z4/Z1. In order to overcome the axial distance, a chain or toothed belt can be used as the chain or belt drive 10.

Fig. 2 shows a side view of the first embodiment variant according to fig. 1, viewed from the right, from which the outer peripheries of the different transmission components are clear. In the side view, the front components are marked with solid lines, while the rear, planar components are shown with dashed lines. The dotted lines in turn represent the more rearward planar members. The direction of travel of the electric bicycle is also indicated by an arrow. From this view, exemplary lubricating oil concepts become clear. The toothed wheels Z1 and Z3 can be immersed, for example, in an oil sump of the housing 2 and thereby entrain lubricating oil into the respective tooth contact or chain contact.

Numerical examples are described below. Value 50 may be assumed as the gear ratio of harmonic drive WG. The fixed gear ratio of the first planetary gear set PS 1 as a superposition gearing may be minus 2. Thus, the torque transmission ratio from the sun gear 11 to the carrier 12 is about 3, and the torque transmission ratio from the ring gear 13 to the carrier 12 is 1.5. The transmission ratio from the driven device of the electric bicycle to the rear wheel is 1.125. The wheel circumference of the rear wheel was 2.1 m. The 2-stage spur gear ratio from the first electric drive EM 1 to the sun gear 11 is 17. Efficiency is neglected in the numerical example below. This information is not precise.

An exemplary driving situation at start-up, in which a relatively high torque of 150Nm is applied by the driver on the human powered drive shaft 1. All rotational speeds are 0. The torque at the second electric drive EM2 is zero, since the driver exerts a large pedal force without any assistance. The torque at the sun gear 11 is 50 Nm. The torque at the first electric drive EM 1 is 3 Nm. The torque at the ring gear 13 is 100 Nm. The torque at the rear wheels is 113 Nm.

The same driving situation, assisted only by the second electric drive EM2, will be described below. The torque applied by the driver on the human powered drive shaft 1 is 50 Nm. The torque at the second electric drive EM2 is 2Nm and 100Nm is obtained after the harmonic drive WG, which is a fixed drive. 150Nm is again applied with the driver. The torque at the second electric drive EM2 is equal to the torque at the rear wheels.

In other driving circumstances a pedal frequency of 60rpm, a pedal torque of 16Nm, i.e. a driver generating 101 watts of power, is obtained when driving at a speed of e.g. 25km/h and at a higher power (e.g. 350 watts of total power) e.g. on an uphill slope. The second electric drive EM2 easily provides 0.13Nm of assistance, i.e. 40W of power, at 3000 rpm. The rotational speed at the rear wheel is 198rpm, the rotational speed at the ring gear 13 is about 223rpm, the rotational speed at the sun gear 11 is about minus 266rpm (backward rotation) and the rotational speed at the first electric drive EM 1 is about minus 4530rpm (backward rotation). The torque at the planet carrier 12 results from the sum of the torque of the second electric drive EM2 and the driver, i.e. 6.5Nm plus 16Nm equals 22.5 Nm. The torque at the sun gear 11 is 7.5Nm, i.e. the torque at the first electric drive EM 1 is 0.43 Nm. The torque at the ring gear 13 is 15Nm and the torque at the rear wheels is 17 Nm. The first electric drive EM 1 has a power of 209W. The total power of the driver and the first and second electric drive EM 1, EM2 is 350W.

In other driving situations, for example in driving at over 25km/h, no electrical assistance is permitted. The first electric drive EM 1 must support the torque applied by the driver at the sun gear 11 of the superposition transmission and therefore introduce electrical power as a mandatory factor. It is precisely this power that must be generated by the second electric drive EM2 acting as a generator, since it cannot be drawn from the battery. This corresponds to a battery-neutral (battery-neutral), power-split operating mode in which the second electric drive EM2 acts in a braking manner.

Examples of relevant values are: assuming that the running power is 30km/h, 200W, the pedal frequency is 70rpm, the driver's pedal torque is 27Nm (power of 200W is obtained), the rotation speed of the first electric drive EM 1 is negative 5540rpm, the torque of the first electric drive EM 1 is about 0.21Nm, the power of the first electric drive EM 1 is about 121W, the power to be generated of the second electric drive EM2 is about negative 121W, the rotation speed of the second electric drive EM2 is about 3500rpm and the torque is negative 0.33Nm, and the power to be output of the second electric drive EM2 is about negative 121W.

Fig. 3 shows an exemplary second embodiment variant of the drive mechanism. In contrast to the first embodiment variant according to fig. 1, the second gear Z1 of the second stage of the 2-stage spur gear drive or of the 2-stage spur gear drive is arranged in a radially nested manner on the first planetary gearset PS 1. In this way, a reduced overall length in the axial direction of the manual drive shaft 1 is achieved. Another advantage results from the following: the larger gear Z3 of the second stage of the spur gear arrangement is located more inwardly of the housing 2 than the gear Z4 of the first stage and the housing 2 may be inclined slightly outwardly.

Fig. 4 shows an exemplary third embodiment variant of the drive mechanism. The difference from the first embodiment variant according to fig. 1 is that instead of the chain or belt drive 10, an intermediate gear Z6 is used. The intermediate gear Z6 can be mounted, for example, on the rotor shaft or rotor 3 of the first electric drive EM 1.

Fig. 5 shows a side view of a third embodiment variant, from which the advantageous lubrication concept described with reference to fig. 2 results.

Fig. 6 shows a fourth embodiment variant of the drive mechanism, wherein the difference from the first embodiment variant is that: the human powered driveshaft 1 is connected to the ring gear 13 of the first planetary gearset PS 1 as a transfer transmission and the driven device 5 is connected to the planet carrier 12. Thus interchanging the connections. The following advantages are thereby obtained: the connection between the human powered drive shaft 1 and the ring gear 13 and the connection between the human powered drive shaft 1 and the harmonic drive WG may be implemented in a common member. Another advantage results from the following: the first gear Z3, which is the second stage of the spur gear system of the first fixed gear system, is located further inward at the housing 2 than the second gear Z4 and the housing 2 can be tilted slightly outward. In order to support a higher torque at the sun gear 11 of the first planetary gearset PS 1, a higher transmission ratio can be formed by the first fixed transmission or the first electric drive EM 1 can be designed with a higher torque.

A fifth embodiment of the drive mechanism is shown in fig. 7. The difference from the first embodiment variant according to fig. 1 is that: instead of the harmonic drive WG, a planetary drive or a second planetary gearset PS2 is used as a second fixed drive for the second electric drive EM 2. In the example shown, the second planetary gear set PS2 is embodied with multi-stage planetary gears to form the highest possible gear ratio. The multi-stage planetary gear in this embodiment has two planetary gears supported on the planetary gear carrier 14, one of which meshes with the ring gear 16 of the second planetary gear set PS2, and the other of which meshes with the sun gear 15 of the second planetary gear set. The following advantages are obtained here: the planet carrier 14 of the second planetary gear set PS2 and the ring gear 13 of the first planetary gear set PS 1 can be implemented as a common member and can be connected to the human powered driveshaft 1. The sun gear 15 of the second planetary gearset PS2 is connected to the rotor 4 of the second electric drive EM2, while the ring gear 16 of the second planetary gearset PS2 is fixed to the housing.

A sixth embodiment variant of the drive mechanism is shown according to fig. 8. In contrast to the first embodiment variant according to fig. 1, the third planetary gearset PS3 is used as the first fixed transmission of the first electric drive EM 1. The sun gear 17 of the third planetary gear set PS3 is connected to the rotor 3 of the first electric drive EM 1. The ring gear 18 of the third planetary gearset PS3 is fixed to the case, and the carrier 19 of the third planetary gearset PS3 is connected to the first gear Z4 of the second stage of the spur gear transmission.

A seventh embodiment variant of the drive mechanism is illustrated in fig. 9, wherein the difference from the second embodiment variant according to fig. 3 is that: a single-stage spur gear is assigned to the first electric drive EM 1 as a first fixed gear. The gear stage is connected to the sun gear 11 of the first planetary gear set PS 1. For this purpose, the first electric drive EM 1 is designed to have a greater torque. Due to the single-stage spur gear, the first electric drive EM 1 can be provided with a greater overall length, since the second spur gear stage is omitted. A simpler mechanism is obtained in an advantageous manner. The gear Z2 of the spur gear stage can be connected to the gear Z1 by means of a chain drive or a belt drive. Alternatively, an intermediate gear 6 can also be provided.

List of reference numerals

1 man power driving shaft or pedal bearing crankshaft

2 casing or pedal bearing casing

3 rotor of a first electric drive

4 rotor of a second electric drive

5 driven means or sprocket or pulley

6 wave generator

7 inner sleeve

8 outer sleeve

9 auxiliary shaft

10-belt or chain drive

11 sun gear of a first planetary gear set

12 planet carrier of a first planetary gear set

13 Ring gear of a first planetary gear set

14 planet carrier of the second planetary gear set

15 sun gear of the second planetary gear set

16 ring gear of second planetary gear set

17 sun gear of third planetary gear set

18 Ring gear of third planetary gear set

19 planet carrier of a third planetary gear set

First electric drive with large EM 1 size

Second electric drive with smaller EM2 size

Harmonic drive with WG as the second fixed drive

First planetary gear set with PS 1 as superposition transmission device

PS2 second planetary gear set as second fixed gearing

PS3 third planetary gear set as first fixed transmission device

Second gear of second stage of Z1 spur gear transmission

First gear of first stage of Z2 spur gear transmission

Second gear of first stage of Z3 spur gear transmission

First gear of second stage of Z4 spur gear transmission

Z6 intermediate gear