Drive device for electric bicycle and assembly for electric bicycle

Abstract

The invention relates to a driving device for an electric bicycle and an assembly for an electric bicycle. In at least one embodiment, the drive device (100) has a planetary gearbox with a planet carrier (20) and a bevel gear stage (3) with a first bevel gear (30). The planet carrier and the first bevel gear are coupled together in a rotationally fixed manner. The planet carrier and the first bevel gear are rotatably mounted by means of a radial bearing (4) about an axis of rotation (A). The radial bearing is supported by the planet carrier.

Description

Technical Field

[0001] A drive unit for an electric bicycle is described. Additionally, components for the drive unit of an electric bicycle, a method for assembling the drive unit of an electric bicycle, and the electric bicycle itself are described. Background Technology

[0002] Bicycles are a cost-effective, easy-to-use, and emission-free mode of transportation. They have also become popular as sports and fitness equipment, with certain types proving particularly well-suited for a variety of sporting applications.

[0003] In recent years, there has been a growing enthusiasm for electric bicycles (especially so-called "electric-assist bicycles"), despite their higher weight and price compared to conventional bicycles. In the case of electric bicycles, providing a reliable drive mechanism is crucial.

[0004] One task is to determine a drive mechanism for an electric bicycle that facilitates efficient and low-wear operation. Other tasks include determining the components for such a drive mechanism, methods for assembling it, and the electric bicycle incorporating it. Summary of the Invention

[0005] First, the drive mechanism used in electric bicycles will be described in detail.

[0006] In at least one embodiment, the drive unit has a planetary gearbox with a planetary carrier and a bevel gear stage with a first bevel gear. The planetary carrier and the first bevel gear are connected to each other in a rotationally fixed manner. The planetary carrier and the first bevel gear are mounted in a manner rotatable about a rotational axis by means of radial bearings. The radial bearings are supported by the planetary carrier.

[0007] This invention is specifically based on the understanding that the performance of a drive unit can be improved through precise and stable alignment of the meshing bevel gears in a bevel gear series. During operation, the bevel gears are subjected to significant forces, particularly large tilting moments.

[0008] By using radial bearings supported by a planetary carrier instead of bevel gears, the tilting moments acting on the first bevel gear and planetary carrier can be absorbed particularly well. For example, the radial bearing can then be selected to be larger than when it is supported by the first bevel gear, and therefore absorb a larger load. Additionally, the radial bearing can be positioned further away from the engagement between the bevel gears, which reduces the load on the radial bearing. This effectively counteracts the tilting and radial displacement of the first bevel gear. Furthermore, the use of radial bearings supported by planetary carriers helps reduce tension due to tolerances.

[0009] In the drive unit, the planet carrier and the first bevel gear are mounted in a manner that allows them to rotate about an axis of rotation. This specifically means that the planet carrier and the first bevel gear can rotate relative to the housing of the drive unit. Unless otherwise stated, the direction parallel to the axis of rotation of the planet carrier is referred to herein and hereinafter as the “axial direction” or simply “axial.” Furthermore, unless otherwise indicated, the directional terms “radial” and “azimuth” refer to this axis of rotation. The planet carrier and / or the first bevel gear are formed, for example, rotationally symmetrically with respect to the axis of rotation.

[0010] In addition to the planet carrier, the planetary gearbox includes planetary gears rotatably mounted on the planet carrier, as well as a ring gear and a sun gear. The planetary gears mesh with the sun gear and the ring gear. The ring gear may be fixed to the housing in a rotationally fixed manner, meaning that the ring gear does not rotate during operation. The sun gear rotates, for example, about the same axis of rotation as the planet carrier. The axes of rotation of the planetary gears extend parallel to or substantially parallel to the axis of rotation of the planet carrier. During operation, the axes of rotation of the planetary gears rotate about the axis of rotation of the planet carrier. The planet carrier may be made of metal. The planetary gears may be partially made of plastic.

[0011] For example, the planetary gears are mounted in a manner that allows them to rotate relative to the planet carrier via needle roller bearings. The use of needle roller bearings helps to counteract the tilting of the planetary gears relative to the planet carrier.

[0012] To allow the planetary gears to be rotatably mounted on the planet carrier, the planetary gears may have bolts or pins that insert through or into recesses in the planet carrier. Alternatively, the planet carrier may have bolts or bushings that insert through holes in the planetary gears.

[0013] A planetary gearbox may have two or more planetary gears, for example, three planetary gears. All planetary gears are then rotatably mounted on a planet carrier. Specifically, each planetary gear is rotatably mounted on the planet carrier via needle roller bearings. All features disclosed for one planetary gear are also disclosed for all other planetary gears in the planetary gearbox.

[0014] The planet carrier and the first bevel gear are connected in a fixed manner in terms of rotation. This means that during normal operation, the planet carrier and the first bevel gear cannot rotate relative to each other about the axis of rotation, but always rotate together at the same rotational speed.

[0015] The planet carrier and the first bevel gear are connected together, for example, via a direct connection in a rotationally fixed manner. The direct connection between the first bevel gear and the planet carrier can be a form-fit connection and / or a force-fit connection. Alternatively, a rotationally fixed connection can also be established by means of auxiliary elements, such as screws and / or nuts.

[0016] The rotary mounting of the planetary carrier and the first bevel gear is achieved by means of a radial bearing. Only one radial bearing can be used for the rotary mounting. However, it is preferable to use another bearing for the rotary mounting.

[0017] Radial bearings are supported by planetary carriers, or in other words, planetary carriers are supported within radial bearings. This means that the radial bearings are arranged on or attached to the planetary carriers and can be in direct contact with them. For example, the inner ring of a radial bearing rests on and is in direct contact with the planetary carrier. Similarly, additional bearings can be supported by planetary carriers, i.e., additional bearings are arranged on or attached to the planetary carriers and, in particular, are in direct contact with them.

[0018] For example, the first bevel gear does not carry a radial bearing; that is, there is no radial bearing arranged on or at the first bevel gear. The connection between the first bevel gear and the radial bearing is established, for example, only via a planetary carrier.

[0019] The bevel gear stage also includes a second bevel gear that meshes with the first bevel gear. During operation, the second bevel gear rotates, for example, about a rotation axis that extends at an angle to or perpendicular to the rotation axis of the planet carrier or the first bevel gear. The bevel gear stage is, for example, a 90° bevel gear stage. The first bevel gear is, for example, a bevel pinion. The second bevel gear is, for example, a ring gear.

[0020] According to at least one embodiment, a segment of the first bevel gear is embedded in the planet carrier. Therefore, this segment is conformally enclosed by the planet carrier. In other words, the planet carrier surrounds the segment of the first bevel gear flush with or in a form-fitting manner. An embedding establishes a connection between the planet carrier and the first bevel gear. Specifically, the connection is non-releasable or cannot be released without destruction. The segment of the first bevel gear is, for example, a pin-shaped segment, such as a cylindrical segment or a conical segment.

[0021] The portion of the first bevel gear can be enclosed by the planet carrier by forming or by one-time forming, particularly by forging, casting, injection molding, or sintering. The planet carrier can be at least partially a one-time formed component, particularly a cast component, an injection molded component, or a sintered component; that is, the planet carrier is at least partially manufactured by casting, particularly metal casting, or by injection molding or sintering.

[0022] According to at least one embodiment, the connection between the first bevel gear and the planetary carrier is a force-fit connection and / or a form-fit connection. For example, the connection is a pure force-fit, a pure form-fit, or a pure force and form-fit.

[0023] The first bevel gear and the planetary carrier connected thereto can form a form-fit connection in the circumferential direction to ensure reliable torque transmission during operation and to transmit higher torques than a purely force-fit connection. Alternatively or additionally, the first bevel gear and the planetary carrier can also form a force-fit connection in the axial direction. For example, the portion of the first bevel gear embedded in the planetary carrier, or the planetary carrier itself, has at least one groove into which a rib of the planetary carrier or the first bevel gear protrudes. The depth of the groove or the height of the rib extends in the radial direction. The groove and the rib extend, for example, in the axial direction. The embedded portion of the first bevel gear can also have a knurled surface.

[0024] According to at least one embodiment, the connection between the first bevel gear and the planetary carrier is partially or completely material-locked. Therefore, the material-locking portion can be an addition or alternative to force-fit and / or form-fit. The material-locking portion can be produced by molding or one-piece molding.

[0025] According to at least one embodiment, the planet carrier and the first bevel gear are directly connected to each other by means of a threaded connection. For example, the first bevel gear is screwed into the planet carrier, or the planet carrier is screwed into the first bevel gear. The threaded connection provides the advantage that no additional components are required for the connection.

[0026] Alternatively, it is conceivable that the first bevel gear and the planetary carrier are connected together in a rotationally fixed manner via a spline connection, whereby the plunger connection is secured by additional screws and / or nuts. For the spline connection, the planetary carrier and / or the first bevel gear may have splined teeth extending axially and / or radially. Alternatively, the first bevel gear and the planetary carrier may be connected to each other by a purely force-fit connection, wherein the force-fit connection is established by means of auxiliary elements, such as screws and / or nuts.

[0027] According to at least one embodiment, the first bevel gear has external threads for a threaded connection. Therefore, the planet carrier has internal threads for a threaded connection. Specifically, the planet carrier includes a recess, such as a hole, into which the first bevel gear is screwed. The internal threads of the planet carrier are then disposed in the region of the recess. The recess extends, for example, in an axial direction, wherein the axis of rotation of the planet carrier extends within the recess. The shape of the recess may be cylindrical. The z-axis of the associated cylindrical member extends, for example, parallel to or coincides with the axis of rotation of the planet carrier. The thread of the first bevel gear is, for example, a left-hand thread to prevent the threaded connection from loosening during operation.

[0028] The first bevel gear has, for example, a pin-shaped section or a cylindrical section, which includes external threads and is screwed into a recess. The teeth of the first bevel gear, which meshes with the teeth of the second bevel gear, are arranged outside the recess of the planetary carrier.

[0029] According to at least one embodiment, the first bevel gear is centered relative to the planet carrier by means of a centering collar. The planet carrier and / or the first bevel gear may have a centering collar for centering. The centering collar is a section, such as an edge or protrusion, of the planet carrier and / or the first bevel gear, at which the planet carrier and the first bevel gear engage with each other, thereby axially and / or radially aligning or centering the planet carrier and the first bevel gear relative to each other. The planet carrier and the first bevel gear may, for example, be in direct contact at the centering collar, and may also press against each other (press fit).

[0030] The surface of the centering collar in direct contact with the planet carrier and the first bevel gear is at least partially radially oriented, meaning that the normal to this surface has a radial component. In particular, the planet carrier and the first bevel gear are radially aligned or centered relative to each other by means of the centering collar.

[0031] The centering collar is, for example, a section of the planet carrier located in the recessed region. For example, the teeth of the first bevel gear are in direct contact with the planet carrier at the centering collar. The teeth of the first bevel gear here and below refer to the teeth used for meshing with the second bevel gear.

[0032] According to at least one embodiment, the centering collar is cylindrical. This means that the surface of the centering collar is cylindrical, where the planet carrier and the first bevel gear are in direct contact and, where applicable, pressed against each other. The z-axis of the associated cylindrical member extends, for example, parallel to or coincides with the axis of rotation of the planet carrier.

[0033] According to at least one embodiment, the diameter of the centering collar is at least the same as the diameter of the teeth of the first bevel gear. For example, the diameter of the centering collar is at least the same as the maximum diameter of the teeth of the first bevel gear.

[0034] According to at least one embodiment, the diameter of the centering collar is larger than the diameter of the thread on the planetary carrier for threaded connection. In particular, the average diameter of the centering collar is larger than the average diameter of the thread on the planetary carrier.

[0035] For example, the diameter of the centering collar is at least 1.2 times or at least 1.5 times the diameter of the thread of the planetary carrier. The thread of the planetary carrier or the first bevel gear has, for example, a diameter of at least 10 mm and / or at most 18 mm, such as 14 mm. The diameter of the centering collar is, for example, at least 15 mm and / or at most 25 mm, such as 19.5 mm.

[0036] By selecting a centering collar with a large diameter, the first bevel gear can be aligned and installed relative to the planetary carrier with specific precision and stability.

[0037] According to at least one embodiment, a centering collar is axially arranged between the threaded connection engagement and the engagement between the first bevel gear and the second bevel gear. The threaded connection engagement is the area where the threads of the planet carrier and the first bevel gear engage with each other. The engagement between the first and second bevel gears is the area where the teeth of the two bevel gears engage with each other. The described relative arrangement facilitates optimal use of the available installation space.

[0038] According to at least one embodiment, the centering collar is at least partially conical in shape. Specifically, the surface of the centering collar has a conical shape, at which the planet carrier and the first bevel gear directly contact and, where applicable, press against each other. This centering collar allows for easy press-fitting between the planet carrier and the first bevel gear.

[0039] According to at least one embodiment, the planet carrier and the first bevel gear are press-fitted together in the region of the centering collar. This means that the first bevel gear and the planet carrier press against each other at the centering collar. This press-fit can be achieved, for example, by applying an increased force when screwing the planet carrier and the first bevel gear together.

[0040] According to at least one embodiment, the radial bearing is located at least partially in the radial direction at the same height as the ring gear of the planetary gearbox. This means that there is a region of the radial bearing, for example, an outer ring, in which the radial bearing is radially spaced from the axis of rotation of the planet carrier by the same distance as the region of the ring gear, for example, the teeth of the ring gear. Alternatively or additionally, the radial bearing may be located at least partially in the radial direction at the same height as at least one planet gear of the planetary gearbox. In particular, the radial bearing protrudes beyond at least one planet gear in the radial direction. For example, the radial bearing also protrudes beyond the planet carrier in the radial direction.

[0041] Such a large radial bearing was chosen for the planetary carrier, thus providing particularly good support for the first bevel gear to prevent tilting.

[0042] According to at least one embodiment, the radial bearing is directly coupled to both the planetary carrier and the drive unit housing. Specifically, the radial bearing abuts the housing and the planetary carrier in the radial direction. For example, the outer ring of the radial bearing abuts the housing in the radial direction, and the inner ring of the radial bearing abuts the planetary carrier in the radial direction. In the region where the radial bearing abuts the housing in the radial direction, the housing, for example, is formed with a single wall, and its surface opposite the radial bearing forms the outer surface of the drive unit.

[0043] Since radial bearings are adjacent to both the housing and the planetary carrier in the radial direction, the tolerance chain in the radial direction is also kept small, which also keeps the maximum tilt angle of the planetary carrier small.

[0044] According to at least one embodiment, the drive unit further includes an axial bearing, and the planetary carrier and the first bevel gear are rotatably mounted by means of the axial bearing. The axial bearing is particularly effective in absorbing axial forces. For example, the axial bearing can absorb forces acting due to tilting moments.

[0045] The radial and axial bearings are specifically arranged in the axially opposite regions of the planetary carrier, that is, the planetary carrier is partially arranged between the radial and axial bearings in the axial direction.

[0046] According to at least one embodiment, the axial bearing has an elongated rolling element. The longitudinal axis of the rolling element extends, for example, in the radial direction in each case. The rolling element of the axial bearing can be cylindrical or tapered. The axial bearing can be a needle roller bearing. The radial bearing is, for example, a ball bearing.

[0047] According to at least one embodiment, the axial bearing is arranged radially on the outer periphery of the planet carrier. This means that the axial bearing is arranged on the planet carrier as far away as possible from the axis of rotation of the planet carrier. This results in a particularly large support width for the axial bearing.

[0048] According to at least one embodiment, the axial bearing and the planetary gears of the planetary gearbox are at least partially at the same height in the radial direction. In other words, there exists a region of the axial bearing that is spaced radially from the axis of rotation of the planet carrier by a distance as far as the region of at least one planetary gear. Specifically, the radial bearing is further radially away from the axis of rotation of the planet carrier than from the axis of rotation of the planetary gears. Alternatively or additionally, the axial bearing and the ring gear of the planetary gearbox are at least partially at the same height in the radial direction.

[0049] According to at least one embodiment, the axial clearance of the planetary carrier in the drive unit is at most 0.3 mm, at most 0.2 mm, or at most 0.1 mm. This means that during operation, the planetary carrier can shift at most 0.3 mm, at most 0.2 mm, or at most 0.1 mm in a direction parallel to the axis of rotation. This small axial clearance of the planetary carrier also keeps the maximum angle at which the planetary carrier can tilt during operation very small. This small axial clearance can be achieved, in particular, by a small tolerance chain in the axial direction. The axial movement of the planetary carrier is limited by stops provided on two sides of the planetary carrier in the axial direction.

[0050] According to at least one embodiment, the thrust washer of the axial bearing is directly opposite the support element of the drive unit in the axial direction. The support element, for example, forms one of the two stops described above. For example, the support element is part of the housing or fixed relative to the housing, i.e., arranged in a non-movable manner relative to the housing. The support element may, in particular, be a radially extending section of the housing. The thrust washer is the washer of the axial bearing on which the rolling elements of the axial bearing roll.

[0051] The fact that the two elements are opposite each other in the axial direction means that, when viewed parallel to the axis of rotation of the planet carrier, one element at least partially covers the other. In other words, the two elements are at least partially at the same height in both the radial and azimuth directions. The fact that the elements are directly opposite each other means that, apart from gaps filled at most with air or lubricant, no other elements, especially no other solid bodies containing the drive mechanism, are arranged between the elements.

[0052] According to at least one embodiment, another thrust washer of the axial bearing is directly opposite the planet carrier in the axial direction. In particular, the planet carrier is spaced apart from the support element in the axial direction by the axial bearing.

[0053] According to at least one embodiment, the ring of the radial bearing is axially opposed to another support element of the drive mechanism. This other support element forms the other of the two stops mentioned above. Specifically, the other support element is part of the housing or fixed relative to the housing, i.e., arranged in a non-movable manner relative to the housing. The other support element is, for example, a radially extending housing segment. The ring is specifically the outer ring of the radial bearing. The rolling elements of the radial bearing operate on the ring.

[0054] According to at least one embodiment, another ring of the radial bearing is directly opposite the planet carrier in the axial direction. This other ring is specifically the inner ring of the radial bearing. This other ring can be spaced apart from the planet carrier by an O-ring. The rolling elements of the radial bearing operate on this additional ring.

[0055] According to at least one embodiment, some or all of the aforementioned elements that are directly opposite each other are adjacent to each other. At least, the sum of the axial distances between the aforementioned elements that are directly opposite each other is at most 0.3 mm, at most 0.2 mm, or at most 0.1 mm. Since only the axial bearing and the radial bearing are arranged axially between the planet carrier and the two support elements, the tolerance chain in the axial direction remains small, thereby achieving low axial clearance of the planet carrier.

[0056] According to at least one embodiment, the radial bearing is arranged axially between the axial bearing and the second bevel gear. In particular, the radial bearing is arranged at least partially at the height of the planet carrier in the axial direction.

[0057] According to at least one embodiment, the planetary gear is arranged axially between the radial bearing and the axial bearing.

[0058] According to at least one embodiment, the support width of the axial bearing is greater than the axial distance between the radial bearing and the engagement portion of the bevel gears in the bevel gear stage. This is specifically used to keep the axial force absorbed by the axial bearing as low as possible. The engagement portion of the bevel gears is understood herein as the area where the teeth of the two bevel gears mesh with each other.

[0059] According to at least one embodiment, the inner diameter of the radial bearing is larger than the inner diameter of the axial bearing. For example, the inner diameter of the radial bearing is at least 4 cm or at least 5 cm.

[0060] By positioning the radial bearings away from the axis of rotation, the planetary carrier can be precisely aligned and stably maintained in its radial position during operation. Large radial bearings also help counteract tilting.

[0061] According to at least one embodiment, the drive device further includes an electric motor and an output terminal. The electric motor is connected to the output terminal via a planetary gearbox to transmit torque from the electric motor to the output terminal.

[0062] In other words, planetary gears connect the electric motor and the output drive. A planetary gearbox is specifically configured to increase the torque transmitted by the electric motor. For example, the planetary gearbox is axially positioned between the electric motor and the output.

[0063] An electric motor consists of a stator and a rotor. For example, an electric motor is an internal rotor motor.

[0064] The output end is a component of the drive unit, through which torque is transmitted from the drive unit. For example, the output end includes an output shaft. The output shaft can be a hollow shaft. For example, the pedal shaft of the drive unit extends through the output shaft. The output shaft can be connected to the chain links or chain link star frame in a rotationally fixed manner. Alternatively or additionally, the output shaft has a joint for engagement with the chain links or chain link star frame.

[0065] According to at least one embodiment, a bevel gear stage connects the planetary gearbox to the output end. In other words, the bevel gear stage connects the planetary gearbox and the output end. The bevel gear stage is configured, for example, to further increase the torque transmitted by the planetary gearbox. The planetary gearbox is, for example, arranged axially between the electric motor and the bevel gear stage.

[0066] According to at least one embodiment, the second bevel gear is connected to the output end without an intermediate gear stage. The rotation axis of the planetary carrier lies, for example, in a plane perpendicular to the rotation axis of the output end. The rotation axis of the output end is, for example, parallel to or the same as the rotation axis of the second bevel gear. The drive device is, for example, an orthogonal drive.

[0067] According to at least one embodiment, the second bevel gear is connected to the output end via a flywheel. For example, the flywheel connects the second bevel gear to the output shaft at the output end.

[0068] According to at least one embodiment, the output shaft at the output end is connected to the pedal shaft of the drive unit via a flywheel. The flywheel is, for example, a toothed disc flywheel. In particular, the pedal shaft passes through the output shaft, wherein the output shaft is formed as a hollow shaft.

[0069] According to at least one embodiment, the pedal shaft extends obliquely or perpendicularly relative to the rotation axis of the planetary carrier. In other words, the rotation axis of the pedal shaft is obliquely or perpendicularly relative to the rotation axis of the planetary carrier. For example, the angle between the pedal shaft and the rotation axis of the planetary carrier, or the angle between the rotation axis of the pedal shaft and the rotation axis of the planetary carrier, is between 80° and 100°, including 80° and 100°.

[0070] Next, the electric bicycle will be described. The electric bicycle includes a drive mechanism according to one embodiment of the exemplary embodiments described herein.

[0071] Next, components for a drive unit for an electric bicycle and a method for assembling the drive unit will be described in detail. Specifically, the components are configured for assembling a drive unit according to one embodiment described herein. In this regard, all features disclosed in connection with the drive unit are also disclosed for the components and methods, and all features disclosed in connection with the components and methods are also disclosed for the drive unit.

[0072] In at least one embodiment, the drive unit for an electric bicycle includes a planetary carrier for a planetary gearbox and a first bevel gear for a bevel gear stage. The planetary carrier and the first bevel gear are connected to each other in a rotationally fixed manner. The planetary carrier and the first bevel gear are mounted in a manner rotatable about a rotational axis by means of radial bearings. The radial bearings are supported by the planetary carrier.

[0073] In addition to the planetary carrier, radial bearing, and first bevel gear, the assembly may include a housing portion, such as a bottom support housing. The planetary carrier and first bevel gear are mounted such that they are rotatable relative to this housing portion. The housing portion of the assembly may be connected to one or more other housing portions of one or more other assemblies to form a housing for a drive mechanism. Furthermore, the assembly may have at least one planetary gear and one ring gear. Additionally, the assembly may include an axial bearing, by which the planetary carrier and first bevel gear may also be rotatably mounted. Furthermore, the assembly may include a pedal shaft.

[0074] Another component includes, for example, an output terminal and a second bevel gear for the bevel gear stage coupled to the output terminal. Another component also includes a housing portion, such as a cover.

[0075] Another component includes, for example, an electric motor having a stator, a rotor, and a motor shaft. Another component may include a support element for a thrust washer used in an axial bearing. Furthermore, another component includes a housing portion, such as a motor housing.

[0076] In at least one embodiment, the component and another component are connected to each other, particularly by connecting their housing portions, for example by screwing them together for assembly of a drive unit. Additionally, the bevel gear of the component and the bevel gear of the other component engage with each other. Furthermore, for example, the pedal shaft of the component is driven through the output shaft of the other component.

[0077] According to at least one embodiment, the component is connected to another component in this method. Specifically, housing portions are connected to each other. In doing so, for example, the support element of the other component, formed by the housing portion of the other component, is arranged axially opposite to the thrust washer of the axial bearing. During assembly, the motor shaft can be inserted through the planetary carrier.

[0078] In the following sections, the drive unit, components, methods for assembling the drive unit, and electric bicycle described herein are explained in more detail with reference to the accompanying drawings, based on exemplary embodiments. The same reference numerals indicate the same elements in the various figures. Since elements or components in the various figures are functionally identical, their descriptions will not be repeated in each of the following figures. For clarity, corresponding reference numerals may not be provided for elements in all figures. Attached Figure Description

[0079] Figure 1 An exemplary implementation of an electric bicycle is shown.

[0080] Figure 2 An exemplary embodiment of the drive device is shown.

[0081] Figure 3 Another exemplary embodiment of the drive device is shown.

[0082] Figure 4 Showing from Figure 3 Details

[0083] Figures 5 to 10 Another exemplary embodiment of the drive device is shown.

[0084] Figure 11 Details of another exemplary embodiment from the drive device are shown.

[0085] Figure 12 An exemplary implementation of the component is shown.

[0086] Figure 13 An exemplary implementation of yet another component is shown.

[0087] Figure 14 The locations in an exemplary embodiment of the assembly method are shown.

[0088] Figure 15 An exemplary implementation of another component is shown.

[0089] Figure 16 Another location is shown in an exemplary embodiment of the assembly method.

[0090] Figure 17 Another exemplary embodiment of the drive device is shown. Detailed Implementation

[0091] Figure 1 An electric bicycle 200 with a bicycle frame 110 is schematically shown, the bicycle frame 110 having a lower frame section 120. The lower frame section forms a downtube. The lower frame section 120 extends toward the bottom bracket of the electric bicycle, wherein the bottom bracket includes a pedal axle 90. The pedal axle 90 is part of a drive unit 100 mounted in the bicycle.

[0092] Figure 2 A first exemplary embodiment of the drive unit 100 is shown in cross-sectional view. The drive unit 100 has a planetary gearbox 2. The planetary gearbox 2 includes a planet carrier 20, which is mounted in a housing 7 such that the planet carrier 20 is rotatable about a rotation axis A. One or more planetary gears 21 are mounted on the planet carrier 20 such that one or more planetary gears 21 are rotatable relative to the planet carrier 20. Figure 2 Only the portion of the drive unit 100 above the rotation axis A is shown.

[0093] The planetary gearbox 2 also includes a sun gear 26. At least one planet gear 21 meshes with the sun gear 26, and the sun gear 26 is also mounted, for example, to be rotatable about a rotation axis A. Additionally, at least one planet gear 21 meshes with a ring gear 27 of the planetary gearbox 2. The ring gear 27 can be mounted to be rotatable about a rotation axis A, or it can be connected to the housing 7 in a rotationally fixed manner; that is, the ring gear 27 can be mounted to be non-rotatable.

[0094] The planetary gearbox 2 connects the electric motor 1 to the output end 8 via an intermediate bevel gear stage 3. The electric motor 1 includes a rotor 11 and a stator 12. The motor shaft 10 of the electric motor 1 is fixed in rotation to the sun gear 26 of the planetary gearbox 2. Alternatively, the motor shaft 10 may also be fixed in rotation to the ring gear 27. The output end 8 is fixed in rotation to the second bevel gear 31 of the bevel gear stage 3. In particular, the output shaft 80 of the output end 8, which is formed as a hollow shaft 80, is fixed in rotation to the bevel gear 31 and is connected, for example, to a chain link or a chain link star (not shown).

[0095] The planetary carrier 20 is connected to the first bevel gear 30 of the bevel gear stage 3 in a rotationally fixed and direct manner. This connection is established by means of a threaded connection 231. The pin-shaped section of the first bevel gear 30 is screwed into a recess in the planetary carrier 20. The pin-shaped section has external threads, and the recess in the planetary carrier is limited by internal threads. The threads are, for example, M14 threads.

[0096] A cylindrical centering collar 230 is provided for centering the first bevel gear 30 relative to the planet carrier 20. The diameter of the centering collar 230 is, for example, 19.5 mm.

[0097] During operation, the planetary carrier 20 and the first bevel gear 30 rotate together about the rotation axis A. The first bevel gear 30 meshes with the second bevel gear 31 of the bevel gear stage, which rotates about the rotation axis P during operation.

[0098] Planetary gearbox 2 and bevel gear stage 3 in drive unit 100 are used to transmit torque from electric motor 1 to output terminal 8. With the help of planetary gearbox 2 and bevel gear stage 3, speed decreases and torque increases. The transmitted torque can be used to assist the pedaling motion of the electric bicycle rider. In this case, the pedal shaft 90 on which the rider manually applies torque is connected to output shaft 80 via flywheel 92, so that both the torque applied by the rider and the torque applied by electric motor 1 can be transmitted to output terminal 8.

[0099] The rotational support of the planetary carrier 20 within the housing 7 is achieved by means of two radial bearings 4, both of which are supported by the planetary carrier 20. Each radial bearing 4 includes an inner ring 42 resting on the planetary carrier, a rolling element 40, for example in the form of balls, and an outer ring 41. The outer ring 41 is adjacent to the housing 7 in the radial direction.

[0100] Due to the arrangement of the first bevel gear 30 directly connected to the planet carrier 20, and the mounting of the planet carrier 20 and the first bevel gear 30 by means of a bearing 4—which is supported by the planet carrier 20 but not by the first bevel gear 30—the first bevel gear 30 can be positioned particularly precisely and stably, and tilting is well prevented during operation.

[0101] Figure 3 Another exemplary embodiment of the drive unit 100 is shown in cross-sectional view. The drive unit 100 includes a housing 7 having three interconnected housing portions 70, 71, and 74. Housing portion 70 forms a motor housing in which an electric motor 1 is housed. Housing portion 71 forms a bottom support housing in which, among other things, a planetary gearbox 2 is housed. The motor housing 70 and the bottom support housing 71 are connected to each other via a sealing sleeve 72. Housing portion 74 forms an output-side cover that is screwed onto the bottom support housing 71.

[0102] The electric motor 1 includes a stator 12 and a rotor 11. The electric motor 1 is an internal rotor type motor. During operation, the rotor 11 rotates relative to the stator 12 or the housing 7 about a rotation axis A. The rotor 11 is coupled to a motor shaft 10 and also causes the motor shaft 10 to rotate about a rotation axis A during operation. The rotation axis A extends through the motor shaft 10. The motor shaft 10 is made, for example, of stainless steel or surface-hardened steel. The electric motor 1 is mounted in the housing 7 by means of a motor bearing 16.

[0103] The motor shaft 10 protrudes axially from the rotor 11 and into the planet carrier 20 of the planetary gearbox 2. In the opposite axial direction, a magnet 14 is arranged at the end of the motor shaft 10, spaced apart from the motor shaft 10 by a connector 15. The connector 15 is made of, for example, aluminum and is intended to reduce the influence of the steel motor shaft 10 on the magnetic field generated by the magnet 14. The drive unit 100 also includes a sensor (not shown) that detects the magnetic field of the magnet 14 and thereby qualitatively and quantitatively detects the position of the motor shaft 10.

[0104] The planetary gearbox 2 forming the first gear stage of the drive unit 100 includes a planet carrier 20, three planetary gears 21, a sun gear 26, and a ring gear 27. Figure 3 The first planetary gear 21, i.e., the planetary gear above the axis of rotation A, is shown in cross-sectional view, while the other planetary gear 21 is shown in top view. The planetary gears 21 are mounted on the planet carrier 20 such that they are rotatable. Similarly, the planet carrier 20 is mounted such that it is rotatable about the axis of rotation A by means of two roller bearings 4, 5. In the present case, the planet carrier 20 has bushings 25 inserted through holes in the planetary gears 21.

[0105] The sun gear 26 for the planetary gearbox 2 is integrated into the motor shaft 10, meaning the motor shaft 10 and the sun gear 26 are integrally formed or shaped into a single piece. Specifically, the teeth of the sun gear 26 are formed in the motor shaft 10 by means of a forming process, such as rolling. This means that the teeth of the sun gear 26 are manufactured without milling, which can be identified by the absence of milling marks. The teeth of the sun gear 26 are helical, meaning they do not extend parallel to the axis of rotation A, but are oblique to or helical around the axis of rotation A.

[0106] The teeth of the sun gear 26 mesh with the corresponding helical teeth of the planet gear 21. Rotation of the motor shaft 10 causes the planet gear 21 to rotate, which in turn causes the planet carrier 20 to rotate about the axis of rotation A. The planet gear 21 rolls on a fixed ring gear 27. The ring gear 27 is fixed to the housing 7, for example, and therefore does not rotate relative to the housing 7 during operation.

[0107] The molding process used in the manufacturing of the teeth of the sun gear 26 results in a particularly smooth tooth surface. The teeth of the planetary gear 21 are made of plastic, for example. When plastic is used for the planetary gear 21, the smooth surface of the sun gear 26 is particularly advantageous because it minimizes wear. Planetary gears made entirely or partially of plastic are more tolerant of manufacturing tolerances and less sensitive to tilting relative to the planet carrier 20.

[0108] In fact, the tilting torque acts on planetary gear 21, which tends to tilt planetary gear 21 relative to planet carrier 20. This tilting torque is largely generated by the use of helical teeth. However, helical teeth are advantageous in terms of high power transmission and low noise generation.

[0109] To minimize and effectively counteract the tilt of the planetary gears 21 relative to the planet carrier 20, each planetary gear 21 is rotatably mounted on the planet carrier 20 by means of a needle roller bearing 22. The needle-shaped or cylindrical rolling elements 24 of the needle roller bearing 22 roll on a bushing 25 on one side and on a sleeve 23 on the other side. The bushing 25 and sleeve 23 are made of, for example, metal. The sleeve 23 is part of the planetary gear 21 and is encapsulated or overmolded with plastic, thereby forming the teeth of the planetary gear 21 with this plastic. By reducing the relative tilt between the planetary gears 21 and the planet carrier 20 due to the use of the needle roller bearings 22, wear on the drive unit 100 can be reduced and its performance improved.

[0110] The planetary carrier 20 has a recess at its axial end opposite to the motor 1. The rotation axis A extends through this recess. The planetary carrier 20 has internal threads in the region of the recess. The first bevel gear 30, i.e., the pinion, of the bevel gear stage 3 is screwed into these internal threads. The bevel gear stage 3 forms the second gear stage of the drive unit 100. The first bevel gear 30 has a cylindrical section with external threads and a conical section with external teeth. The cylindrical section is screwed into the recess of the planetary carrier 23, thereby securing the first bevel gear 30 to the planetary carrier 23 and making it immovable relative to the planetary carrier 20; that is, the first bevel gear 30 is fixed to the planetary carrier in a rotationally fixed manner. The first bevel gear 30 is precisely aligned relative to the planetary carrier 20 by means of a centering collar. The conical section protrudes axially from the planetary carrier 20 away from the electric motor 1.

[0111] The first bevel gear 30 has a recess that opens in the direction of the electric motor 1, and the motor shaft 10 is guided into the recess. The motor shaft 10 can rotate freely within the recess. Figure 3 Unlike what is depicted, the motor shaft 10 can be rotatably mounted in the recess by means of a bearing.

[0112] The section of the motor shaft 10 that protrudes into the recess of the bevel gear 30 has no teeth. This section, for example, forms an engagement for a so-called "independent" test of the electric motor 1, i.e., a test in the uninstalled state.

[0113] During operation, the planetary carrier 20 and the first bevel gear 30 rotate together about the rotation axis A. The bevel gear stage 3 has a second bevel gear 31 in the form of a ring gear. The second bevel gear 31 is mounted such that it can rotate about the pedal axis P, which extends perpendicular to the rotation axis A. Therefore, the bevel gear stage 3 is a 90° bevel gear stage.

[0114] The second bevel gear 31 is connected via a flywheel 81 to an output shaft 80, which is in the form of a hollow shaft. The output shaft 80 is part of the output end 8. The output end 8 also includes, for example, chain links and / or chain link star brackets (not shown) that are fixed in rotational direction to the output shaft 80. Alternatively, the output shaft 80 may also have only a joint for fixed rotational connection with the chain links or chain link star brackets.

[0115] The pedal shaft 90 extends through the hollow shaft-shaped output shaft 80. The pedal shaft 90 is connected to the output shaft 80. The pedal shaft 90 and the output shaft 80 are rotatably mounted by means of radial bearings 60, 61, also known as main bearings 60, 61. When the rider of the electric bicycle pedals, the pedal shaft 90 rotates about the pedal axis P and drives the output shaft 80 via a flywheel. The electric motor 1 applies torque to the output shaft 80 via a planetary gearbox 2 and a bevel gear stage 3 to assist the rider. The drive unit 100 shown is an orthogonal drive.

[0116] By using a bevel gear stage 3 directly coupled to the planet carrier 20, i.e., coupled to the planet carrier 20 without any additional intermediate gear stages, the drive unit 100 can be designed to be particularly compact while simultaneously providing efficient speed reduction from the electric motor 1 to the output end 8. However, the direct coupling between the planet carrier 20 and the bevel gear stage 3 also results in the bevel gear stage 3 applying axial, radial, and azimuthal forces to the planet carrier 20 during operation of the drive unit 100. These forces attempt to push the planet carrier 20 towards the electric motor 1 and simultaneously tilt the planet carrier 20.

[0117] To effectively absorb the acting radial force, the planetary carrier 20 is mounted in the housing 7 via a large radial bearing 4. The radial bearing 4 has an inner diameter of, for example, 5 cm. The radial bearing 4 is supported by the planetary carrier 20.

[0118] The resulting axial force is absorbed by the axial bearing 5. Specifically, the tilting moment acting on the planetary carrier 20 results in a large axial load on the axial bearing 5. The axial bearing 5 also has a large diameter. Here, the axial bearing 5 is arranged at the outer edge or periphery of the planetary carrier 20, i.e., as far apart as possible radially from the axis of rotation A. Furthermore, elongated rolling elements, such as cylindrical or tapered elements, are used as the rolling elements 50 of the axial bearing 5, thereby distributing the load over a larger area.

[0119] To minimize tilting of the planetary carrier 20, the axial clearance between the radial bearing 4 and the axial bearing 5 is kept particularly small, for example, a maximum of 0.1 mm. This is achieved, in particular, by a small tolerance chain in the axial direction. The small tolerance chain is achieved as follows: the thrust washer 51 of the axial bearing 5 is arranged axially opposite to the radial extension of the support element, i.e., the motor housing 70, and the rolling element 52 rolls on the thrust washer 51. Another thrust washer 52 of the axial bearing 5 is arranged axially opposite to the planetary carrier 20. Furthermore, the inner ring 42 of the radial bearing 4 is arranged axially opposite to the planetary carrier 20, and the rolling element 40 of the radial bearing 4 rolls on the inner ring. The outer ring 41 of the radial bearing 4 is arranged axially opposite to another support element, i.e., a portion of the bottom support housing 71. The motor housing 70 and the bottom support housing 71 are connected to each other in an axially immovable manner. The elements that are axially opposite to each other are abutted against each other or spaced apart from each other by at most a narrow gap in the axial direction. In particular, the sum of the axial distances between the aforementioned opposing elements is less than 0.1 mm.

[0120] When the drive unit 100 is installed and the motor is running, the planetary carrier 20 is pressed axially toward the electric motor 1. The planetary carrier 20 then axially abuts directly against the thrust washer 52, and the thrust washer 51 axially abuts directly against the motor housing 70. This small axial distance ensures that the planetary carrier 20 remains almost completely tilt-free, despite a strong tilting moment.

[0121] Another measure to reduce the tilt of the planet carrier 20 is the small radial clearance between the planet carrier 20 and the first bevel gear 30. For this purpose, the first bevel gear 30 is securely connected to the planet carrier 20. The radial clearance of the planet carrier 20 is kept low by the fact that the radial bearing 4 for radial mounting of the planet carrier 20, arranged radially between the planet carrier 20 and the housing 7, abuts against the planet carrier 20 with its inner ring 42 and against the housing 7 with its outer ring 41 in the radial direction. No intermediate elements are used between the radial bearing 4 and the housing 7, as these elements could increase the radial clearance of the planet carrier 20 or the first bevel gear 30. In other words, the radial clearance between the first bevel gear 30 and the planet carrier 20 is kept low by using fewer elements in the radial tolerance chain. This means that the planet carrier 20 can only tilt to a limited extent.

[0122] In summary, the use of the aforementioned radial bearing 4 and axial bearing 5 helps to counteract the tilting of the planetary carrier 20 and effectively absorb forces. This makes the drive unit 100 particularly powerful while ensuring low wear.

[0123] Performance is further enhanced by the precise alignment of bevel gears 30 and 31. This is achieved, on the one hand, through the low-clearance mounting of the planetary carrier 20 and the first bevel gear 30, and on the other hand, through the low-clearance mounting of the second bevel gear 31. For this purpose, the second bevel gear 31 is fixedly, i.e., immovably, connected to the output shaft 80. The output shaft 80 is mounted via a radial bearing 60 such that it can rotate about the axis of rotation P, wherein the radial bearing 60 is in direct contact with both the output shaft 80 and the cover 74. The cover 74 is then securely connected to the bottom support housing 71. Similarly, to reduce the clearance of the second bevel gear 31 in the axial direction parallel to the axis of rotation A, the rotatable mounting of the second bevel gear 31 about the axis of rotation P is achieved through a small number of movable elements between the housing 7 and the second bevel gear 31.

[0124] The fixed connection between housing parts 71 and 74 is a threaded connection. For this threaded connection, the bottom support housing 71 and the cover 74 have interlocking threads 710 and 740. These threads 710 and 740 extend about the axis of rotation P of the pedal shaft 90. The relative arrangement between housing parts 71 and 74 is secured by a fixing element 742. In this case, the fixing element 742 is a screw screwed into the receiving portion 741 of the housing part 74. Specifically, housing part 74 has two annular segments 743 and 744, which, in the shown cross-sectional view, are formed by the U-shaped region of the third housing part 74; that is, the two annular segments 743 and 744 are spaced apart from each other by a gap in a direction parallel to the axis of rotation P. Each of the two segments 743 and 744 forms a portion of the external thread 740 of the housing part 74. The longitudinal end of the screw 742 presses the second section 744 away from the first section 743, thereby causing the threaded connection between the housing parts 71 and 74 to lock and thus securing the housing parts 71 and 74 in their relative arrangement.

[0125] The second bevel gear 31 has its movement relative to the third housing element 74 in a direction parallel to the axis of rotation P limited by a stop surface. Therefore, the threaded connection between housing portions 71 and 74 allows the second bevel gear 31 to be positioned with particularly high precision along the axis of rotation P. The secure threaded connection then ensures a particularly stable position of the second bevel gear 31 in the direction of the axis of rotation P. In general, the bevel gears 30 and 31 are then aligned with each other with a specific precision, which benefits the performance of the entire drive unit 100.

[0126] Figure 4 It shows Figure 3 The details are as follows. Here, one can see in detail how the teeth of the first bevel gear 30 press against the cylindrical centering collar 230 of the planet carrier 20, so that the first bevel gear 30 is stably and precisely centered relative to the planet carrier 20. It can also be seen that a tool engagement portion for connecting with a tool, such as a drill bit or screwdriver, is arranged on the side of the first bevel gear 30 facing away from the planet carrier 20.

[0127] Figure 5 Another exemplary embodiment of the drive device 100 is shown. (Compared to...) Figure 3 Unlike other types of gears, the centering collar 230 is conical rather than cylindrical. This allows for easy press-fitting between the first bevel gear 30 and the planet carrier 20.

[0128] Figure 6An exemplary embodiment of the drive unit 100 is shown, wherein a rotationally fixed connection between the first bevel gear 30 and the planet carrier 20 is established by means of an additional screw 32 or bolt 32. The screw 32 or bolt 32 is screwed into the threads in the first bevel gear 30, thereby axially pressing the first bevel gear 30 against the planet carrier 20. The planet carrier 20 and the first bevel gear 30 are centered relative to each other by means of a centering collar 230. The screw or bolt 32 has a conical section that is received in and abuts against a conical bore in the planet carrier 20. When the screw or bolt 32 is tightened, the planet carrier 20 and the bevel gear 30 are particularly securely connected to each other.

[0129] exist Figure 7 In the exemplary embodiment shown, the planet carrier 20 and the first bevel gear 30 are connected together in a rotationally fixed manner via splines. The splines are secured by a hollow nut 33, which is screwed into the first bevel gear 30, thereby axially clamping the planet carrier 20 between the first bevel gear 30 and the hollow nut 33. The teeth of each spline extend in the axial direction.

[0130] exist Figure 8 In the exemplary embodiment shown, the axially protruding protrusion of the planetary carrier 20 has two stepped portions, one of which forms a centering collar 230, and the other of which has an external thread through which a direct threaded connection 231 with the first bevel gear 30 is established.

[0131] exist Figure 9 In, with Figure 7 Unlike other gears, this one does not have splines with axially extending teeth; instead, it has splines with radially extending teeth. The splines are secured by screws 32, i.e., the planetary carrier 20 is axially clamped between the head of the screw 32 and the first bevel gear 30.

[0132] Figure 10 It shows the relationship with Figure 6 The embodiments shown are similar to exemplary embodiments. However, in this case, there is also a form fit between the first bevel gear 30 and the bushing 25 of the planet carrier 20.

[0133] Figure 11 It shows the relationship with Figure 3 and Figure 4 Details of exemplary embodiments of drive devices similar to the drive device shown in the diagram. However, with Figure 3 and Figure 4 Conversely, the tool engagement portion of the first bevel gear 30 is not located on the side away from the planet carrier 20, but on the side facing the planet carrier 20.

[0134] Figure 12 It shows the use of Figure 3 An exemplary embodiment of the drive unit assembly 101 is described. Assembly 101 includes a bottom support housing 71, a planetary carrier 20, and a first bevel gear 30, which are connected to each other in a rotationally fixed manner and rotatably mounted by means of a radial bearing 4 carried by the planetary carrier 20. Assembly 101 also includes a planetary gear 21, which is rotatably mounted on the planetary carrier 20 by means of a needle roller bearing 22. An axial bearing 5 is arranged on the side of the planetary carrier 20 opposite to the first bevel gear 30. Additionally, a pedal shaft 90 is inserted through the bottom support housing 71. The bottom support housing 71 is made of metal, for example. The bottom support housing 71 is formed as a single piece and encloses the pedal shaft 90 in the direction about the pedal axis P and the planetary carrier 20 in the direction about the rotation axis A.

[0135] Figure 13 It shows the use of Figure 3 An exemplary embodiment of another component 102 of the drive unit 100. Component 102 includes a motor housing 70, in which an electric motor 1 having an associated motor shaft 10 is housed.

[0136] In order to assemble Figure 3 The drive unit 200 first connects component 102 to component 101. The resulting device is... Figure 14 As shown in the diagram. During connection, the motor shaft 10 is pushed through the planetary carrier 20 into the receiving portion of the first bevel gear 30. Additionally, the thrust washer 51 is arranged axially opposite the radially extending section of the motor housing 70. The dimensions of the various components are selected such that there is no air gap or only a small air gap in the axial direction between the housing sections: bearings 4 and 5 can be axially supported on the housing sections.

[0137] Figure 15 It shows the assembly Figure 3 An exemplary embodiment of another component 104 of the drive unit 100. Component 104 includes a housing portion 74. A fastening element 742 in the form of a screw is inserted into a receiving portion 741 of the housing portion 74, but only to the extent that segments 743, 744 are not yet clamped relative to each other. Component 104 also includes a bevel gear 31, an output shaft 80, and a radial bearing 60. The bevel gear 31 and the output shaft 80 are mounted via the radial bearing 60 such that they are rotatable about a rotation axis P.

[0138] In order to assemble the drive unit, now will Figure 15 The component 104 shown is screwed onto Figure 14 On the device shown in the image (see Figure 16To this end, the pedal shaft 90 is pushed through the feed passage 745 in the housing portion 74. Housing portions 74 and 71 are screwed together until the bevel gears 30 and 31 are positioned in a direction parallel to the axis of rotation P as needed. Then, screw 742 is tightened, thereby clamping sections 743 and 744 relative to each other and thus locking the threaded connection between housing portions 74 and 71. In this way, the bevel gears 30 and 31 can be fixed in their relative positions parallel to the axis of rotation P.

[0139] Figure 17 An exemplary embodiment of the drive device 100 is shown, which is associated with... Figure 2 The difference in the drive unit 100 shown is that there is no threaded connection between the planet carrier 20 and the first bevel gear 30. Instead, the pin-shaped section of the first bevel gear 30 is embedded in the planet carrier 20 and is thus conformally enclosed by the planet carrier 20. The planet carrier 20 is a one-piece molded component, such as a cast component. The centering collar can be omitted.

[0140] List of reference numerals in the attached figures

[0141] 1. Electric motor

[0142] 2 Planetary Gearbox

[0143] 3 Bevel Gear Stage

[0144] 4 Radial bearings

[0145] 5 Axial bearings

[0146] 7. Casing

[0147] 8 Output terminals

[0148] 10 Motor Shaft

[0149] 11 Rotors

[0150] 12 stators

[0151] 14 Magnets

[0152] 15 Adapters for magnets

[0153] 16 Motor bearings

[0154] 20 planetary carriers

[0155] 21 Planetary Gears

[0156] 22 Needle roller bearings

[0157] 23. Outerwear

[0158] 24 Rolling elements

[0159] 25 Bushing / Bolt

[0160] 26 Sun Gears

[0161] 27. Ring gear

[0162] 30 First bevel gear / conical pinion

[0163] 31 Second bevel gear / ring gear

[0164] 40 Rolling elements

[0165] 41 Outer Ring

[0166] 42 Inner Ring

[0167] 50 Rolling elements

[0168] 51 Thrust Washer

[0169] 52 Thrust Washer

[0170] 60 radial bearing

[0171] 61 Radial bearing

[0172] 70 Motor housing

[0173] 71 Bottom support housing

[0174] 72 Sealing Sleeve

[0175] 74 Covering

[0176] 80 Output Shaft

[0177] 81 Flywheel

[0178] 90 pedal shaft

[0179] 92 Flywheel

[0180] 100 drive unit

[0181] 101 components

[0182] 102 components

[0183] 104 components

[0184] 110 Bicycle Frame

[0185] 120 lower pipe

[0186] 200 electric bicycles

[0187] 710 thread

[0188] 740 thread

[0189] 741 Reception Department

[0190] 742 Fixing Components / Screws

[0191] 743 Part One

[0192] 744 Part Two

[0193] 745 feedthrough section

[0194] A. Rotation axis

[0195] P Pedal axis / rotation axis

[0196] 32 Screws or bolts

[0197] 33 Nuts / Hollow Nuts

[0198] 230 Centering Ring

[0199] 231 Threaded connection

Claims

1. Drive arrangement (100) for an electrically powered bicycle (200), the drive arrangement (100) comprising: a planetary gearbox (2) having a planet carrier (20), a bevel gear stage (3) having a first bevel gear (30), wherein the planet carrier (20) and the first bevel gear (30) are coupled to each other in a rotationally fixed manner, the planet carrier (20) and the first bevel gear (30) are mounted in a rotationally rotatable manner about an axis of rotation (A) by means of a radial bearing (4), the radial bearing (4) is supported by the planet carrier (20).

2. Drive arrangement (100) according to claim 1, wherein a section of the first bevel gear (30) is embedded in the planet carrier (20).

3. Drive arrangement (100) according to claim 1, wherein the planet carrier (20) and the first bevel gear (30) are directly connected to each other by means of a threaded connection (231).

4. Drive arrangement (100) according to claim 3, wherein the first bevel gear (30) has an external thread for the threaded connection (231), and the planet carrier (20) has an internal thread for the threaded connection (231).

5. Drive arrangement (100) according to one of the preceding claims, wherein the first bevel gear (30) is centered relative to the planet carrier (20) by means of a centering collar (230).

6. Drive arrangement (100) according to claim 5 insofar as it is dependent on claim 3 or 4, wherein a diameter of the centering collar (230) is greater than a diameter of a thread of the planet carrier (20) for the threaded connection (231).

7. Drive arrangement (100) according to claim 6 or according to claim 5 insofar as it is dependent on claim 3 or 4, wherein the centering collar (230) is arranged axially between an engagement of the threaded connection and an engagement between the first bevel gear (30) and a second bevel gear (31).

8. Drive arrangement (100) according to one of claims 5 to 7, wherein the centering collar (230) is at least partially conically shaped.

9. Drive arrangement (100) according to one of claims 5 to 8, wherein the planet carrier (20) and the first bevel gear (30) are pressed together in the region of the centering collar (230).

10. Drive arrangement (100) according to one of the preceding claims, wherein, the radial bearing (4) is arranged at least partially at the same height in the radial direction as a ring gear (27) of the planetary gearbox (2).

11. Drive arrangement (100) according to one of the preceding claims, wherein the radial bearing (4) is directly coupled both to the planet carrier (20) and to a housing (7) of the drive arrangement (100).

12. Drive arrangement (100) according to one of the preceding claims, further comprising: an axial bearing (5), the planet carrier (20) and the first bevel gear (30) being mounted in a rotatable manner by means of the axial bearing (5).

13. The drive arrangement (100) of claim 12, wherein the radial bearing (4) is arranged axially between the axial bearing (5) and the second bevel gear (31) of the bevel gear stage (3).

14. The drive arrangement (100) of claim 12 or 13, wherein an inner diameter of the radial bearing (4) is larger than an inner diameter of the axial bearing (5).

15. The drive arrangement (100) of one of the preceding claims, further comprising an electric motor (1), an output (8), wherein the electric motor (1) is coupled to the output (8) via the planetary gearbox (2) in order to transmit a torque from the electric motor (1) to the output (8).

16. An assembly (101) for an electric bicycle (200), the assembly (101) comprising a planet carrier (20) for a planetary gearbox (2), a first bevel gear (30) for a bevel gear stage (3), wherein the planet carrier (20) and the first bevel gear (30) are coupled to each other in a rotationally fixed manner, the planet carrier (20) and the first bevel gear (30) are mounted in a rotatable manner about an axis of rotation (A) by means of a radial bearing (4), the radial bearing (4) is supported by the planet carrier (20).

Images