Drive device for a drive unit of an electric bicycle, drive unit and electric bicycle

Abstract

The invention relates to a drive device (10a; 10b) for a drive unit (12a; 12b) of an electric bicycle (14a; 14b), with a bidirectional freewheel (16a; 16b), wherein the freewheel (16a; 16b) comprises at least one clamping element unit (18a, 18b). It is proposed that the clamping element unit (18a; 18b) includes at least one preloading unit (112a; 112b) designed to generate a preload force.

Description

State of the art

[0001] A drive device for a drive unit of an electric bicycle, with a bidirectional freewheel that includes at least one clamping element unit, has already been proposed. Disclosure of the invention

[0002] The invention relates to a drive device for a drive unit of an electric bicycle, with a bidirectional freewheel comprising at least one clamping element unit.

[0003] It is proposed that the clamping element unit comprises at least one preload unit designed to generate a preload force. Preferably, the freewheel is configured as a friction-based freewheel. The clamping element unit is preferably configured as a clamping body unit, a clamping ball unit, or a clamping roller unit. In particular, the freewheel is configured differently from a pawl freewheel. The drive unit preferably comprises an electric motor. The drive unit particularly includes a gearbox for transmitting a drive force from the drive unit to an output pinion of the drive unit. The output pinion is, for example, configured as a chainring or the like. The output pinion is preferably connected to a gearbox output of the gearbox. Preferably, the clamping element unit is arranged at the gearbox output of the drive unit.Alternatively, the clamping element unit could be located in a different position within the gearbox. Alternatively, the drive device could also be used on a vehicle other than an e-bike. This vehicle could include an internal combustion engine, an electric motor, or something similar.

[0004] The drive device preferably comprises at least one power transmission element for transmitting a drive force from the drive unit. The clamping element unit is preferably arranged on the power transmission element. The power transmission element can be, for example, a spur gear, a planetary gear, a ring gear, a sun gear, or another power transmission element that would appear suitable to a person skilled in the art. Preferably, the power transmission element forms the gearbox output of the drive unit. Alternatively, however, it is also conceivable that the power transmission element is arranged within the gearbox and is particularly intended for power transmission to an intermediate shaft of the gearbox. The drive device preferably comprises at least one shaft. Preferably, the shaft is designed as an output shaft.Alternatively, it is also conceivable that the shaft is designed as an intermediate shaft, which is particularly located within the gearbox, or the like. Preferably, the output pinion is rotationally fixed to the shaft designed as the output shaft. It is conceivable that the output pinion is formed integrally with the output shaft. "Integral" can be understood to mean at least a materially bonded connection, for example by a welding process, an adhesive bonding process, an injection molding process, and / or another process that would appear appropriate to a person skilled in the art, and / or advantageously formed in one piece, such as by manufacturing from a single casting and / or by manufacturing using a single- or multi-component injection molding process, and advantageously from a single blank.

[0005] The drive unit preferably comprises at least one crank axle. The crank axle is preferably driven by a user via pedals. The drive device has a forward direction of rotation, which corresponds in particular to the forward movement of the e-bike. The output sprocket is preferably connected to the crank axle such that the output sprocket can be driven by a rotation of the crank axle, in particular at least in one direction of rotation, preferably in the direction of the forward direction of rotation of the drive device. It is conceivable that the shaft is rotatably mounted to the crank axle. Additionally, it is conceivable that the drive unit has a further freewheel, which is arranged between the shaft and the crank axle. The further freewheel is preferably designed to prevent the crank axle from rotating when the shaft is rotating.Alternatively, the shaft could be non-rotatably connected to the crank axle. In particular, it is also conceivable that the shaft could be formed integrally with the crank axle. Furthermore, it is also conceivable that the shaft corresponds to the crank axle. Preferably, the shaft and the power transmission element are arranged coaxially with an axis of rotation of the freewheel. In particular, the shaft, the crank axle, and / or the power transmission element are / are rotatably mounted about the axis of rotation.

[0006] The clamping element unit is preferably configured to interrupt the transmission of a motor torque directed forward (with respect to the forward direction of the electric bicycle) to the shaft, in particular the output pinion, if the rotational speed of the shaft is greater than the rotational speed of the power transmission element driven by the motor torque. It is also conceivable that the clamping element unit is configured to interrupt the transmission of a motor torque directed backward (with respect to the forward direction of the electric bicycle) to the shaft, in particular the output pinion, if the rotational speed of the shaft, in particular the output pinion, is greater than the rotational speed of the power transmission element driven by the motor torque.The clamping element unit is preferably configured to interrupt the transmission of torque from the shaft, particularly the output pinion, to the power transmission element, preferably the gearbox and / or the electric motor, when the shaft, particularly the output pinion, rotates backwards with respect to the forward direction of rotation, particularly the forward direction of the e-bike. The clamping element unit is preferably configured to interrupt the transmission of torque from the shaft, particularly the output pinion, to the power transmission element, preferably the gearbox and / or the electric motor, regardless of the rotational speed of the power transmission element and regardless of the rotational speed of the shaft, particularly the output pinion.

[0007] The clamping element unit preferably comprises at least one clamping element. The clamping element is preferably configured in a clamped state, particularly between the power transmission element and the shaft, to transmit torque between the power transmission element and the shaft. The at least one clamping element is also preferably configured in a state decoupled from the power transmission element and / or the shaft, particularly in a freely rotating state and / or at a distance from the power transmission element and / or the shaft, to interrupt torque transmission between the power transmission element and the shaft. The clamping element is, for example, designed as a rolling element, a clamping body (e.g., non-circular), or the like. Preferably, the clamping element is configured differently from a pawl.It is also conceivable that the clamping element unit comprises a plurality of clamping elements, in particular at least two, preferably at least three, clamping elements.

[0008] The design of the drive device advantageously provides a particularly responsive bidirectional freewheel for the drive unit of an electric bicycle. Advantageously, a particularly quiet bidirectional freewheel for the drive unit of an electric bicycle can be realized. The drive device advantageously enables particularly gentle operation of a drive unit, especially a gearbox and / or an electric motor. Advantageously, unwanted torque transmission from the shaft to the power transmission element can be counteracted by moving the shaft in any direction of rotation. Advantageously, unwanted torque transmission from an output side to the electric motor and / or at least a part of the gearbox can be counteracted.

[0009] Preferably, the clamping element unit is designed to decouple vibrations of a wrapping element. The wrapping element is, for example, a chain, a belt, or the like. The wrapping element is preferably rotationally fixed to the output shaft, in particular the output pinion. The wrapping element is specifically designed to transmit a drive force from the shaft, preferably designed as the output shaft, and in particular from the output pinion, to a drive wheel of the e-bike. The drive wheel is preferably designed as a rear wheel of the e-bike. Alternatively, however, it is also conceivable that the drive wheel is designed as a front wheel of the e-bike.Preferably, the clamping element unit is designed to counteract the transmission of vibrations from the wrapping element to components of the drive unit located downstream of the clamping element unit in the drive train. Preferably, the clamping element unit is designed to counteract the transmission of vibrations from the wrapping element to the gearbox and / or the electric motor. Advantageously, this ensures particularly gentle operation. Advantageously, the use of the clamping element unit can provide a particularly durable drive device, preferably a drive unit, and in particular a particularly durable electric motor and / or a particularly durable gearbox. Advantageously, gearbox rattle can be prevented. Advantageously, the decoupling of vibrations from a wrapping element can be achieved with particularly low noise.

[0010] Preferably, the clamping element unit comprises at least one rolling element, in particular a roller. Alternatively, it is also conceivable that the rolling element is designed as a sphere, a barrel, a needle, a cone, or another body of revolution that would appear suitable to a person skilled in the art. Preferably, the rolling element is rotationally symmetrical. The at least one rolling element is preferably configured in a clamped state to transmit torque between the power transmission element and the shaft. The at least one rolling element is preferably configured in a free-rotating state to interrupt torque transmission between the power transmission element and the shaft. Preferably, the clamping element unit comprises a plurality of rolling elements, in particular at least two, and more preferably at least three.The clamping element unit comprises, for example, at least one sleeve, which is arranged, in particular, on the power transmission element. The sleeve is preferably rotationally fixed to the power transmission element. Preferably, the sleeve is formed integrally with the power transmission element. It is also conceivable that the sleeve is formed by the power transmission element itself. The at least one rolling element is arranged, in particular, between the power transmission element, especially the sleeve, and the shaft. The rolling elements are preferably arranged uniformly. Preferably, a plurality of rolling elements are arranged uniformly along a circumferential direction of the shaft, which preferably runs in a plane perpendicular to the axis of rotation. The drive device preferably comprises at least one bearing unit, which is arranged, at least partially, between the power transmission element, especially the sleeve, and the shaft.The bearing unit is designed, in particular, to mount the power transmission element and the shaft rotatably relative to each other and / or at a fixed radial distance. The bearing unit preferably comprises at least one bearing element, for example, a sliding bearing ring or the like. The at least one bearing element is preferably arranged between the power transmission element, in particular the sleeve, and the shaft. The clamping element unit has, in particular, at least one clamping surface. The power transmission element, in particular the sleeve, preferably has the at least one clamping surface. The clamping surface is designed, in particular, to interact with the at least one rolling element to transmit torque between the power transmission element and the shaft. The clamping element unit preferably has at least one further clamping surface.The additional clamping surface is preferably designed to interact with the at least one rolling element to transmit torque between the power transmission element and the shaft. The shaft preferably has a circular cylindrical surface. The additional clamping surface is preferably formed by the circular cylindrical surface of the shaft. It is particularly preferred that the at least one rolling element be clamped between the power transmission element and the additional clamping surface to transmit torque between the power transmission element and the shaft. The power transmission element, in particular the sleeve, preferably has an inner surface. The inner surface is particularly oriented towards the shaft. The inner surface preferably includes the at least one clamping surface. The power transmission element, in particular the sleeve, preferably has at least one recess for arranging the at least one rolling element.

[0011] The at least one rolling element can be arranged, at least partially, in the at least one recess. Preferably, the clamping surface is arranged in the at least one recess of the sleeve, in particular of the power transmission element. Preferably, a number of recesses correspond to a number of rolling elements of the clamping element unit. Preferably, the at least one recess is asymmetrically designed, in particular at least in a circumferential direction of the power transmission element, which preferably lies in a plane perpendicular to the axis of rotation. Preferably, the at least one recess is designed such that the at least one rolling element can be arranged in the recess in a clamping position against the clamping surface and in a free-rotating position. Advantageously, a particularly responsive bidirectional freewheel can be implemented.A particularly quiet bidirectional freewheel can be advantageously implemented for a drive unit of an electric bicycle.

[0012] Preferably, the clamping element unit comprises a clamping element holder. The clamping element holder preferably has at least one receiving area for the at least one clamping element, in particular the at least one rolling element. The clamping element holder is preferably annular. In particular, the clamping element holder is designed as a cage ring. Preferably, the number of receiving areas corresponds to the number of clamping elements, in particular rolling elements, of the clamping element unit. The receiving areas are preferably arranged separately from one another. The at least one receiving area preferably limits the movement of the at least one clamping element, in particular the at least one rolling element, preferably about the axis of rotation, preferably in the circumferential direction, relative to the clamping element holder. The clamping element holder is preferably arranged between the shaft and the power transmission element, in particular the sleeve.Preferably, the clamping element retaining body is movably arranged relative to the force transmission element, in particular the sleeve, and / or the shaft. In particular, the clamping element retaining body is configured to guide the at least one rolling element. It is conceivable that the clamping element, in particular the rolling element, is arranged spring-free on the clamping element retaining body. Preferably, the at least one receiving area for the at least one clamping element, in particular the at least one rolling element, is free of spring elements. In particular, an area between the at least one clamping element, preferably the at least one rolling element, and the clamping element retaining body, in particular at least in the receiving area, is free of spring elements. Preferably, the at least one clamping element, in particular the at least one rolling element, is free of any bearing on the clamping element retaining body by means of spring elements.Alternatively, it is also conceivable that the at least one clamping element, in particular the at least one rolling element, is spring-mounted on the clamping element holder, preferably in the at least one receiving area. For example, a bearing spring for the spring-loaded mounting of the at least one clamping element is arranged between the at least one clamping element, in particular the at least one rolling element, and the clamping element holder, preferably in the receiving area. The bearing spring is designed, for example, as a bending spring, a torsional spring, a rubber-elastic element, or the like. It is conceivable that the bearing spring is attached to the clamping element holder. It is also conceivable that the bearing spring is formed integrally with the clamping element holder. Advantageously, a particularly reliable function of the clamping element unit can be achieved.Advantageously, a particularly reliable bidirectional freewheel can be provided.

[0013] Preferably, the clamping element unit comprises a mechanical control unit. The control unit is preferably configured to switch between a freewheel state and a torque transmission state of the freewheel. The freewheel state is preferably a state of the freewheel in which torque transmission between the power transmission element and the shaft is interrupted. The torque transmission state is preferably a state of the freewheel in which torque transmission between the power transmission element and the shaft occurs. Preferably, the switch between the freewheel state and the torque transmission state is performed automatically by the control unit, in particular without user intervention and / or without electronic control. The control unit is preferably free of electrical components. Alternatively, however, it is also conceivable that the clamping element unit comprises an electronic control unit.Advantageously, an electrical power supply for controlling the terminal element unit can be dispensed with.

[0014] Preferably, the control unit comprises a friction unit designed to generate an actuating force. The friction unit is specifically designed to move the clamping element holder relative to the power transmission element and / or the shaft, preferably to rotate it about the axis of rotation. Particularly preferably, the friction unit is designed to release the freewheel from a torque transmission state depending on a relative movement of the power transmission element to the shaft. Preferably, the friction unit is designed to switch the freewheel from the torque transmission state to the freewheel state depending on a relative movement of the power transmission element to the shaft by means of the actuating force.The friction unit is specifically designed to position the at least one rolling element relative to the power transmission element, in particular the sleeve, and / or the shaft, preferably to engage the freewheel, preferably at least from the torque transmission state to the freewheel state. The friction unit is designed to generate a frictional force between the clamping element holder and a friction element that is separate from the clamping element holder. Preferably, the friction unit forms a frictional contact between the clamping element holder and the friction element. The friction unit particularly comprises at least one friction element. Preferably, the friction unit includes a plurality of friction elements, preferably at least two, and particularly preferably at least three. The at least one friction element is designed to form the frictional contact between the clamping element holder and the friction element.The at least one friction element preferably has at least one friction surface for forming the frictional contact between the clamping element holder and the friction body. Preferably, the at least one friction element is attached to the clamping element holder. It is conceivable that the at least one friction element is formed integrally with the clamping element holder or separately from the clamping element holder. Alternatively, it is also conceivable that the at least one friction element is attached to the friction body, in particular formed integrally with the friction body. The friction element is preferably designed as a spring-elastic element, a rubber-elastic element, or another friction element that would appear suitable to a person skilled in the art. The friction body is preferably formed by a stationary component of the freewheel. In particular, in at least one embodiment, the friction body is rotationally fixed to a housing component of a drive unit housing.The friction element is designed, for example, as a friction ring or the like. Alternatively, it is also conceivable that the friction element is formed by a stationary component of the e-bike, in particular the drive unit. The friction element is alternatively formed, for example, by a frame element of the e-bike frame, the housing component of the drive unit housing, or the like. Preferably, the actuating force is a frictional force. In particular, the friction unit is designed to generate the actuating force in at least one operating state of the freewheel through static and / or sliding friction between the clamping element retaining body and the friction element. The actuating force, in particular the frictional force, preferably acts against a torque applied to the clamping element retaining body, at least in the operating state of the freewheel.Preferably, the actuating force, preferably the frictional force, is designed to delay rotation of the clamping element retaining body about the axis of rotation relative to the shaft, particularly at least in the free-running state. The clamping element unit is preferably configured to clamp the rolling element in the recess by means of the clamping surface when the rotational speed of the power transmission element in the forward direction is greater than or equal to the rotational speed of the shaft.The friction unit is preferably designed, when the power transmission element rotates in the forward direction, where the rotational speed of the power transmission element is greater than the rotational speed of the shaft, to brake the clamping element retaining body relative to the power transmission element by means of the actuating force, in particular the frictional force, in order to preferably bring the at least one rolling element into contact with the at least one clamping surface in the at least one recess of the power transmission element, in particular the sleeve, and to clamp it. In particular, the clamping element unit is designed, via the actuating force, preferably the frictional force, to generate a force on the at least one rolling element when the shaft rotates backward with respect to the forward direction of rotation, in order to preferably release the at least one rolling element from the at least one clamping surface, so that the freewheel is preferably switched to the freewheeling state.Preferably, the actuating force, in particular the frictional force, causes the at least one rolling element to clamp with the power transmission element, especially the sleeve, and the shaft when the rotational speed of the power transmission element is greater than the rotational speed of the shaft, preferably at least when the power transmission element is rotating forward with respect to the forward direction of rotation. By clamping the at least one rolling element with the power transmission element, especially the sleeve, and the shaft, a torque can preferably be transmitted between the power transmission element and the shaft. The at least one rolling element is preferably rotationally fixed to the power transmission element, especially the sleeve, and the shaft in the torque transmission state. The at least one rolling element is in the clamped position, in particular, when the freewheel is in the torque transmission state.Preferably, the at least one rolling element is arranged to rotate freely in the at least one recess in the freewheeling state. Preferably, the at least one rolling element is in a free-rotating position when the freewheel is in the freewheeling state. In particular, the at least one rolling element is arranged to rotate freely in the at least one recess when the shaft rotates backward with respect to the forward direction of rotation. Preferably, the at least one rolling element is arranged to rotate freely in the at least one recess when the shaft rotates forward with respect to the forward direction of rotation and the rotational speed of the shaft is greater than the rotational speed of the power transmission element. Preferably, the at least one rolling element is arranged to rotate freely in the at least one recess when the power transmission element rotates backward with respect to the forward direction of rotation.The clamping element unit is specifically designed to release at least one rolling element from the clamping position by means of the clamping element retainer when the shaft speed is greater than the speed of the power transmission element. Advantageously, a mechanical control unit for the clamping element unit can be implemented in a simple design. Advantageously, a particularly robust mechanical control system can be provided for the clamping element unit.

[0015] Preferably, the friction unit comprises at least one spring unit. Preferably, the clamping element holder is connected to the friction body via the spring unit. The spring unit is preferably designed to generate a holding force between the clamping element holder and the friction body. More preferably, the spring unit is designed to generate the actuating force, in particular the frictional force, of the friction unit. The spring unit comprises, for example, at least one spring element. Preferably, the at least one friction element is formed by the at least one spring element. It is conceivable that the at least one spring element is designed as a bending spring, a torsion spring, a disc spring, an volute spring, a ring spring, or the like. Alternatively, it is also conceivable that the spring element is designed as a rubber-elastic element. The at least one spring element is preferably arranged on the clamping element holder.Preferably, at least one spring element is arranged between the clamping element holder and the friction element. In particular, the clamping element holder can be connected to the friction element via the at least one spring element. Advantageously, a mechanical control unit for the clamping element unit can be implemented in a simple design. Advantageously, a particularly robust mechanical control unit for the clamping element unit can be provided. Advantageously, a particularly effective frictional contact between the clamping element holder and the friction element can be achieved.

[0016] Preferably, the spring unit comprises at least one bending spring. For example, the at least one bending spring is formed by the at least one spring element. Preferably, the spring unit is free of helical springs. The at least one bending spring is, for example, designed as a leaf spring, a wire spring, in particular as a needle spring, a torsion spring, or the like. Advantageously, a particularly effective frictional contact can be realized between the clamping element holding body and the friction element.

[0017] Preferably, the spring unit comprises at least one leaf spring. Preferably, the at least one leaf spring is formed by the at least one spring element, in particular the at least one bending spring. It is conceivable that the leaf spring is designed as a coil spring, a rebound spring, an elliptical spring, a parabolic spring, a wave spring, or as another leaf spring that would appear suitable to a person skilled in the art. The leaf spring preferably has at least one leaf. In particular, the at least one friction surface of the friction unit is arranged on the at least one spring element, in particular on the leaf spring. Preferably, the friction surface of the friction element is arranged on the at least one leaf. It is conceivable that the leaf spring is designed as a single-leaf or as at least two-leaf leaf springs. It is conceivable that the friction surface extends in the axial direction and / or in the radial direction.It is conceivable that the friction surface is at least partially curved and / or at least partially straight. Preferably, at least one principal plane of extension of the friction surface, which extends at least axially, runs at least substantially parallel to the axial direction. A "principal plane of extension" of a component or element can be understood as a plane that is parallel to a largest side face of the smallest possible imaginary cuboid that just completely encloses the component or element, and which, in particular, passes through the center of the cuboid. "Substantially parallel" here can be understood as an orientation of a direction relative to a reference direction, particularly in a plane, wherein the direction has a deviation from the reference direction of, in particular, less than 8°, advantageously less than 5°, and most advantageously less than 2°.Preferably, at least the main plane of extension of the friction surface, which extends at least radially, runs at least substantially parallel to the radial direction. It is conceivable that the friction surface, particularly the one extending in the axial direction, is oriented radially inwards or radially outwards. It is also conceivable that the friction surface, particularly the one extending in the radial direction, is oriented away from the clamping element holder or the clamping element retaining body, preferably at least in the axial direction. Advantageously, a particularly effective frictional contact can be achieved between the clamping element retaining body and the friction element.

[0018] The leaf spring is designed, for example, as a leaf spring with at least two leaves. Preferably, the leaf spring with at least two leaves has at least two friction surfaces of the friction unit for forming the frictional contact between the clamping element holder and the friction body. In particular, the spring with at least two leaves has at least two leaves. Preferably, one of the friction surfaces is arranged on each leaf. Advantageously, the two-leaf leaf spring allows for a particularly effective frictional contact between the clamping element holder and the friction body. Advantageously, a particularly large friction surface can be achieved.

[0019] The spring unit comprises, for example, at least one spring element, in particular the one already mentioned, which surrounds at least a large portion of the rotational axis of the freewheel, in particular the one already mentioned. The phrase "surrounds at least a large portion of an axis" means, in particular, that the element surrounds at least 55%, preferably at least 65%, preferably at least 75%, particularly preferably at least 85%, and most preferably at least 95% of the axis in a circumferential direction that lies in a plane perpendicular to the axis. The spring element that surrounds at least a large portion of the rotational axis of the freewheel is preferably ring-shaped.It is conceivable that the at least one spring element, which surrounds the rotation axis of the freewheel for at least a large part of its length, has at least a curved profile along its main extent and / or at least some straight sections angled relative to each other along its main extent. Advantageously, a spring unit can be provided that is particularly easy to design. Advantageously, a particularly large number of contact points can be realized between the at least one spring element and the clamping element holder. Advantageously, a particularly large number of contact points can be realized between the at least one spring element and the friction body. Advantageously, a particularly effective and / or uniform frictional contact between the clamping element holder and the friction body can be realized. Advantageously, a spring unit with a particularly small number of components can be realized.Advantageously, the spring unit can be mounted to the clamping element holder in a particularly simple and quick manner.

[0020] The spring unit comprises, for example, at least one spring element, in particular the one already mentioned, with at least one mounting ramp. The mounting ramp is specifically designed to guide the at least one spring element during its installation on the friction body. Preferably, the mounting ramp is designed to make contact with the friction body during installation and, in particular, to guide the spring element as it moves toward a predetermined mounting position. The at least one mounting ramp is preferably arranged on the at least one leaf of the spring element, which is designed as a leaf spring. The mounting ramp is specifically formed by a surface angled to the axis of rotation, preferably not perpendicular. Advantageously, this allows for particularly simple and / or quick installation of the clamping element unit on the friction body.Advantageously, a particularly fast and cost-effective production of a bidirectional freewheel can be achieved with a clamping element unit.

[0021] The spring unit comprises, for example, at least one spring element, in particular the one already mentioned, which is formed separately from the clamping element holder. It is conceivable that the spring element formed separately from the clamping element holder is attached to the clamping element holder or to the friction body, in particular that it is formed integrally with the friction body. It is also conceivable that the spring element formed separately from the clamping element holder is formed at least partially from a material that corresponds to or differs from the material of the clamping element holder. For example, the clamping element holder is made of a plastic. Alternatively, however, it is also conceivable that the clamping element holder is made of a metal or another material that would appear suitable to a person skilled in the art.Preferably, at least one spring element is made of metal. Alternatively, however, it is also conceivable that the spring element is made of plastic or another material that a person skilled in the art would consider suitable. Advantageously, different materials can be used for the at least one spring element and the clamping element holder. Advantageously, the materials for the clamping element holder and the at least one spring element can be selected to be particularly suitable. Advantageously, the materials for the clamping element unit can be selected with particular flexibility, at least with regard to cost, stability, weight, and / or durability.

[0022] The spring unit comprises, for example, at least one spring element, in particular the one already mentioned, which is attached to a body separate from the clamping element holder. The body is preferably a stationary component of the freewheel or the e-bike, especially the drive unit. For example, the body is formed by the housing component of the drive unit, the frame element, or the like. It is conceivable that the body is formed by the friction element. It is conceivable that the at least one spring element is formed integrally with the body or, preferably non-destructively, is detachably attached to the body. Advantageously, the total mass of moving parts of the drive device can be kept low. Advantageously, undesired inertial forces can be kept low. Advantageously, a particularly responsive clamping element unit for the bidirectional freewheel can be provided.

[0023] The spring unit comprises, for example, at least one spring element, in particular the one already mentioned, which is attached to the clamping element holder. For example, the spring element is formed integrally with the clamping element holder, snapped, clamped, screwed, or similarly connected to it. Advantageously, this allows for particularly reliable positioning of the spring element. Advantageously, this also allows for particularly reliable and precise operation of the clamping element unit, preferably the control unit.

[0024] The spring unit comprises, for example, at least one spring element, in particular the one already mentioned, which is integrally formed with the clamping element holder. Advantageously, a particularly robust clamping element unit can be provided. Advantageously, a particularly secure connection between the clamping element holder and the spring elements can be achieved. Advantageously, a control unit for controlling the clamping element unit can be implemented with particularly high reliability.

[0025] The spring unit comprises, for example, at least one spring element, in particular the one already mentioned, which is overmolded by the clamping element holder. Preferably, the spring element is at least partially overmolded by the clamping element holder. Advantageously, a particularly secure connection between the clamping element holder and the spring elements can be achieved. Advantageously, a control unit for controlling the clamping element unit can be implemented with particularly high reliability. Advantageously, the at least one spring element is arranged in a particularly captive manner.

[0026] The friction unit preferably comprises a friction surface extending in the axial direction, in particular the one already mentioned. The axial direction preferably runs parallel to the axis of rotation. Advantageously, a particularly compact design of the drive device can be achieved, at least in the radial direction.

[0027] The friction surface extending in the axial direction is preferably arranged on a side facing the clamping element holder when viewed in the axial direction. Preferably, in at least one embodiment, the at least one spring wing of the spring element is arranged on the side facing the clamping element holder, particularly when viewed at least in the axial direction. Advantageously, a particularly compact clamping element unit for bidirectional freewheeling can be realized.

[0028] The friction surface extending in the axial direction is, alternatively, arranged on a side facing away from the clamping element holder when viewed in the axial direction. Preferably, in at least one embodiment, the at least one spring wing of the spring element is arranged on the side facing away from the clamping element holder, particularly when viewed at least in the axial direction. Advantageously, this allows for particularly simple mounting of the clamping element holder to the friction body.

[0029] In at least one embodiment, the friction surface extending in the axial direction is, when viewed radially, oriented, for example, inwards. Preferably, in at least one embodiment, the at least one friction surface is arranged facing the shaft. In particular, in at least one embodiment, the at least one friction surface is arranged facing the axis of rotation. Advantageously, a particularly compact clamping element unit with a friction unit can be realized. Advantageously, a particularly responsive freewheel with a particularly compact design can be provided.

[0030] The friction unit preferably comprises at least two friction elements, in particular those already mentioned, for generating an actuating force, wherein the friction elements are arranged uniformly in a circumferential direction, which in particular runs in a plane perpendicular to the axis of rotation, of the clamping element holder. Preferably, the friction elements are arranged uniformly in the circumferential direction on the clamping element holder or the friction body. Preferably, the friction elements are formed by spring elements of the spring unit. Alternatively, however, it is also conceivable that the friction elements are arranged unevenly in the circumferential direction, preferably on the clamping element holder or the friction body. Advantageously, a particularly uniform holding force and / or friction force can be achieved between the clamping element holder and the friction body.Advantageously, a particularly reliable and precise function of the clamping element unit can be provided for the bidirectional freewheel.

[0031] The drive device preferably comprises at least one, in particular the previously mentioned, power transmission element for transmitting a drive force from the drive unit, which has at least one through-passage through which the clamping element holder is guided at least partially outwards in a radial direction. It is conceivable that a number of through-passages correspond to a number of friction elements, in particular spring elements. However, it is also conceivable that the number of through-passages differs from the number of friction elements, in particular spring elements. In particular, in at least one embodiment, the at least one friction element, preferably the at least one spring element, is arranged at least partially in the at least one through-passage. In particular, in at least one embodiment, the at least one through-passage is free of friction elements, in particular spring elements.Advantageously, a particularly responsive bidirectional freewheel can be designed to be especially compact. Weight can be advantageously saved by designing the power transmission element with bushings.

[0032] The drive device preferably comprises at least one, in particular the previously mentioned, power transmission element for transmitting a drive force from the drive unit, wherein the power transmission element is designed as a spur gear. The spur gear preferably has external teeth. It is conceivable that the external teeth are designed as straight teeth or as helical teeth. Advantageously, a particularly simple mounting of the clamping element unit to the power transmission element can be achieved.

[0033] Preferably, the maximum diameter of the at least one rolling element is between 6% and 20% of the maximum inner diameter of the force transmission element, particularly the sleeve. More preferably, the maximum diameter of the at least one rolling element is a maximum of 15%, and more preferably a maximum of 10%, of the maximum inner diameter of the force transmission element, particularly the sleeve. Alternatively, it is also conceivable that the maximum diameter of the at least one rolling element is outside the range of 6% to 20% of the maximum inner diameter of the force transmission element, particularly the sleeve. In particular, the inner diameter is measured in the radial direction. Preferably, the maximum diameter of the rolling element is measured in the radial direction. Advantageously, a clamping element unit with a particularly high packing density with respect to the rolling elements can be achieved.Advantageously, the high packing density of the rolling elements in the clamping element holder allows for a particularly reliable and precise bidirectional freewheel.

[0034] The drive device preferably comprises at least one shaft, in particular the one mentioned above, wherein the maximum diameter of one of the rolling elements, in particular the one mentioned above, is between 8% and 25% of the maximum diameter of the shaft. Preferably, the maximum diameter of the at least one rolling element is at most 15%, and more preferably at most 12%, of the maximum diameter of the shaft. Alternatively, however, it is also conceivable that the maximum diameter of the at least one rolling element is outside the range of 8% to 25% of the maximum diameter of the shaft. In particular, the maximum diameter of the shaft is measured in the radial direction. In particular, the maximum diameter of the shaft is at most 38 mm, and more preferably, the maximum diameter of the shaft is 32 mm.Advantageously, a clamping element unit with a particularly high packing density of rolling elements can be achieved. The high packing density of the rolling elements in the clamping element holder allows for a particularly reliable and precise bidirectional freewheel.

[0035] A maximum inner diameter of the power transmission element, particularly the sleeve, is preferably no more than 46 mm. Preferably, the maximum inner diameter of the power transmission element, particularly the sleeve, is between 40 mm and 41 mm. Alternatively, it is also conceivable that the maximum inner diameter of the power transmission element is greater than 46 mm. Advantageously, a particularly compact drive device with a bidirectional freewheel can be provided.

[0036] A maximum diameter of the rolling element, particularly the previously mentioned one, is preferably a maximum of 5 mm. Preferably, the maximum diameter of the rolling element is substantially 3.5 mm. The phrase "a dimension is at least substantially a specified value" means, in particular, that the actual value of the dimension deviates from the specified value by a maximum of 10%, and more preferably by a maximum of 5%. Alternatively, it is also conceivable that the maximum diameter of the rolling element is greater than 5 mm. Advantageously, a particularly compact drive device with a bidirectional freewheel can be provided. Advantageously, a clamping element unit with a particularly high packing density of the rolling elements can be achieved.Advantageously, the high packing density of the rolling elements in the clamping element holder allows for a particularly reliable and precise bidirectional freewheel.

[0037] A maximum angle of movement, in particular a translational angle, of the rolling element relative to the clamping element holder about a rotational axis of the freewheel, particularly the one mentioned above, is preferably a maximum of 1.5°. Preferably, the maximum angle of movement, in particular a translational angle, of the at least one rolling element relative to the clamping element holder is between 0° and 1°. This is particularly true in an embodiment in which the rolling element is spring-mounted on the clamping element holder. Most preferably, the maximum angle of movement, in particular a translational angle, of the at least one rolling element relative to the clamping element holder is substantially 0.5°. Alternatively, however, it is also conceivable that the maximum angle of movement, in particular a translational angle, of the at least one rolling element relative to the clamping element holder about the rotational axis is greater than 1.5°.Advantageously, a particularly responsive and precise bidirectional freewheel can be provided.

[0038] A maximum angle between a clamping position of the rolling element, particularly one mentioned previously, and a maximum free rotation position of the rolling element about a rotation axis of the freewheel, particularly one mentioned previously, is preferably a maximum of 5°. Preferably, the maximum angle between the clamping position of the rolling element and the maximum free rotation position of the rolling element about the rotation axis of the freewheel is a maximum of 2.5°. More preferably, the maximum angle between the clamping position of the rolling element and the maximum free rotation position of the rolling element about the rotation axis of the freewheel is between 0.3° and 2.5°, and particularly preferably between 0.4° and 2°. Most preferably, the maximum angle between the clamping position of the at least one rolling element and the maximum free rotation position of the at least one rolling element about the rotation axis is at least substantially 0.8°.The maximum free rotation position and / or the clamping position of the rolling element is located, in particular, in the at least one recess for the at least one rolling element. The maximum free rotation position and the clamping position are preferably located at opposite end regions of the recess. Preferably, the at least one further clamping surface is arranged on a rearward side of the recess with respect to the forward direction of rotation. Preferably, the free rotation position is arranged on a front side of the recess with respect to the forward direction of rotation. In particular, the recess has a stop for the at least one rolling element in the end region where the free rotation position of the at least one rolling element is located. Specifically, the rolling element is in the maximum free rotation position when the rolling element rests against the stop of the recess.Alternatively, it is also conceivable that the maximum angle between the clamping position and the maximum free-rotating position of the rolling element around the rotational axis of the freewheel is greater than 5°. This can advantageously provide a particularly responsive and precise bidirectional freewheel.

[0039] The clamping element unit and the power transmission element preferably have a common plane of intersection, which runs at least substantially perpendicular to one of the rotational axes of the freewheel, in particular the one mentioned above. "Substantially perpendicular" can be understood as an orientation of a direction relative to a reference direction, wherein the direction and the reference direction, particularly when viewed in a projection plane, enclose an angle of 90° and the angle has a maximum deviation of, in particular, less than 8°, advantageously less than 5°, and most advantageously less than 2°. The clamping element unit is preferably arranged at least partially, and more preferably at least substantially completely, within the power transmission element.The phrase "an element is arranged at least substantially entirely within another element" means, in particular, that the element is arranged within the other element to at least 50%, preferably at least 75%, and especially preferably at least 90% of its total volume and / or total mass. In at least one embodiment, the friction unit, particularly the spring unit, is preferably arranged entirely within the force transmission element. Alternatively, it is also conceivable that the clamping element unit is arranged axially offset from the force transmission element such that at least the external teeth of the force transmission element and the clamping element unit are free from a common plane of intersection that is at least substantially perpendicular to the axis of rotation.Advantageously, a particularly compact drive device with a highly responsive bidirectional freewheel can be provided. Damage, especially contamination, to the clamping element unit can be advantageously prevented.

[0040] The sum of a clamping element retaining body angle and a spring angle is preferably smaller than or equal to a sleeve clearance angle. The clamping element retaining body angle is, in particular, formed by the sum of a clamping element retaining body clearance angle and a clamping element retaining body load angle. The clamping element retaining body angle is preferably a maximum of 2.5°. Particularly preferably, the clamping element retaining body angle is substantially 1.8°. Alternatively, however, it is also conceivable that the clamping element retaining body angle is greater than 2.5°. The clamping element retaining body clearance angle corresponds, in particular, to the maximum angle of movement, especially the translation angle, of the rolling element relative to the clamping element retaining body about the axis of rotation of the freewheel.The clamping element holding body load angle is, in particular, the sum of a mechanical clamping element holding body load angle and a chemical and / or thermal clamping element holding body load angle. The clamping element holding body load angle is preferably a maximum of 1°. Particularly preferably, the clamping element holding body load angle is substantially 0.8°. Alternatively, however, it is also conceivable that the clamping element holding body load angle is greater than 1°. The mechanical clamping element holding body load angle depends, in particular, on possible mechanical deformations of the clamping element holding body during operation of the clamping element unit. The mechanical clamping element holding body load angle is preferably a maximum of 0.7°. Particularly preferably, the mechanical clamping element holding body load angle is substantially 0.5°.Alternatively, it is also conceivable that the mechanical clamping element holding body load angle is greater than 0.7°. The chemical and / or thermal clamping element holding body load angle depends in particular on the clamping element holding body with regard to possible thermal expansion, possible swelling of the material, for example due to moisture absorption, or the like. The chemical and / or thermal clamping element holding body load angle is preferably a maximum of 0.5°. Particularly preferably, the chemical and / or thermal clamping element holding body load angle is substantially 0.3°. Alternatively, however, it is also conceivable that the chemical and / or thermal clamping element holding body load angle is greater than 0.5°. The sleeve clearance angle preferably corresponds to the maximum angle between the clamping position of the at least one rolling element and the maximum free rotation position of the at least one rolling element.The sum of the sleeve clearance angle and a sleeve load angle yields, in particular, a sleeve angle. The sleeve angle is preferably a maximum of 6.5°, more preferably a maximum of 3.5°. Particularly preferably, the sleeve angle is substantially 3.3°. Alternatively, however, it is also conceivable that the sleeve angle is greater than 6.5°. The sleeve load angle is preferably dependent at least on any possible deformation and / or expansion of the force transmission element, in particular the sleeve, preferably the at least one clamping surface, during operation of the clamping element unit. The sleeve load angle is preferably a maximum of 4°, more preferably a maximum of 2°. Most preferably, the sleeve load angle is at least substantially 2.5°. Alternatively, however, it is also conceivable that the sleeve load angle has a value greater than 4°. The spring angle is, in particular, a sum of a spring clearance angle and a spring load angle.The spring angle is preferably a maximum of 0.1°. Particularly preferably, the spring angle is substantially 0.05°. Alternatively, however, it is also conceivable that the spring angle is greater than 0.1°. The spring clearance angle refers in particular to any possible play in the connection between the clamping element retaining body and the spring unit, especially the at least one spring element. The spring load angle depends in particular on any possible bending of the at least one spring element. The spring load angle is preferably a maximum of 0.1°. Particularly preferably, the spring load angle is substantially 0.05°. Alternatively, however, it is also conceivable that the spring load angle is greater than 1°. Advantageously, a particularly reliable function of the clamping element unit for the bidirectional freewheel can be achieved.

[0041] The preload unit is preferably designed to hold or bring the clamping element retaining body in at least one defined position relative to the power transmission element, in particular relative to the recess, and / or relative to the friction unit. The preload unit is preferably designed to enable or disable the bidirectional freewheel, particularly when the shaft rotates backward with respect to the forward direction of rotation. Preferably, the preload unit defines a bidirectional position and a unidirectional position of the clamping element retaining body relative to the power transmission element, in particular relative to the recess, and / or relative to the friction unit.In the bidirectional position, the clamping element holder is arranged relative to the recess such that the clamping element, in particular the rolling element, is prevented from becoming trapped between the clamping surfaces during movement towards them due to premature contact of the clamping element with a wall of the clamping element holder that defines the receiving area. In the bidirectional position of the clamping element holder, torque transmission between the power transmission element and the shaft is preferably prevented during a rotation of the shaft in the reverse direction relative to the forward direction of rotation.In the unidirectional position, the clamping element holder is arranged relative to the recess such that the clamping element, in particular the rolling element, remains spaced away from a wall of the clamping element holder that defines the receiving area when moving towards the clamping surfaces, thus allowing the clamping element to be clamped between the clamping surfaces. In the unidirectional position of the clamping element holder, torque transmission between the power transmission element and the shaft is preferably enabled when the shaft rotates in the opposite direction to the forward rotation. Activation or deactivation of the bidirectional freewheel is preferably achieved by moving the power transmission element.The movement of the power transmission element required to activate or deactivate the bidirectional freewheel depends in particular on the operating state before a change to a rotation of the shaft that is reversed with respect to the forward direction of rotation.

[0042] The preload unit is preferably arranged on the clamping element holder. To exert a force on the clamping element holder, the preload unit is preferably supported by the power transmission element, the friction unit, and / or the housing component. The preload unit can be connected to the clamping element holder and / or the power transmission element, the friction unit, or the housing component, particularly by a material bond, especially by welding, be formed in one piece, or be positively and / or force-fitted to them. The preload unit is preferably elastically designed, for example, due to its shape and / or material. In particular, the preload unit is designed such that, in at least one operating state of the drive device, the preload unit counteracts any relative movement of the clamping element holder with respect to the power transmission element and / or the friction unit.

[0043] The inventive design advantageously allows a bidirectional freewheel to be combined with a fully requested roller freewheel, and in particular, enables the selection of whether or not torque is transmitted during a reverse movement of the shaft, depending on the situation. Furthermore, the position of the clamping element can be predetermined for a significantly larger number of situations and / or operating changes. In particular, there are advantageously few situations in which the position of the clamping element is unknown. Specifically, the clamping element assumes a defined position during freewheeling, shortly before torque transmission, thus minimizing the risk of slippage. In particular, the e-bike's backward roll on a slope can be reliably prevented, as the preload unit already establishes a force equilibrium for torque transmission and the clamping element is advantageously engaged early.

[0044] It is further proposed that the clamping element unit comprises at least one mechanical control unit, in particular the one already mentioned, wherein the control unit comprises a friction unit, in particular the one already mentioned, which is designed to generate an actuating force, in particular the one already mentioned, and wherein the control unit comprises the at least one preload unit. The preload force is preferably an additional force to the actuating force. Preferably, the actuating force and the preload force work together to bring and / or hold the clamping element holding body in a defined position. The preload force and the actuating force preferably have different points of application on the clamping element holding body. The preload force is preferably designed to modify the actuating force, in particular to make it direction-dependent. The actuating force on its own, as a frictional force, is typically direction-independent.The preload force is preferably designed to support the actuating force in an accelerating direction and to weaken it in a retarding direction. The accelerating direction is, for example, at least substantially parallel or antiparallel to the forward direction of rotation. The retarding direction is, for example, at least substantially antiparallel or parallel to the forward direction of rotation. The design according to the invention allows the position of the clamping element and / or the clamping element retaining body to be advantageously and reliably determined when switching between different operating states of the drive device.

[0045] It is further proposed that the friction unit and the preload unit are arranged such that the actuating direction of the friction unit and the direction of action of the preload force are preferably oriented transversely, and in particular at least substantially perpendicularly, to each other. The actuating direction is preferably determined by the spring unit of the friction unit. The actuating direction preferably runs at least substantially perpendicular to the actuating force, and in particular at least substantially parallel to the radial direction of the drive device. The direction of action of the preload force preferably acts at least substantially parallel or tangentially to the circumferential direction. Preferably, the preload unit is designed and / or arranged separately, differently, and in particular at a distance from the spring unit. The design according to the invention allows the preload unit to be advantageously compact and, in particular, advantageously precisely matched to the actuating force.

[0046] It is further proposed that the preload unit comprises at least one spring element. Preferably, the preload unit comprises several spring elements, in particular at least two. In particular, the preload unit comprises one spring element for each or every two spring elements of the friction unit. Alternatively, the number of spring units of the friction unit differs from the number of spring elements of the preload unit. The spring elements of the preload unit are preferably arranged circumferentially at various, in particular uniformly distributed, points of application of the clamping element holder. In particular, the drive device is designed to be rotationally symmetrical with respect to the spring elements of the preload unit. Alternatively, the preload unit comprises exactly one spring element, or the spring elements are arranged at points of application of the clamping element holder that are irregularly distributed circumferentially.The spring elements of the preload unit are preferably identical in design. Alternatively, the preload unit comprises at least two differently designed spring elements. The design according to the invention allows the preload unit to be implemented in a structurally advantageously simple and robust manner.

[0047] It is further proposed that at least one spring element be designed as a compression spring. The compression spring can be cylindrical, conical, barrel-shaped, waist-shaped, or arc-shaped. The spring travel of the compression spring is preferably oriented at least substantially parallel or tangentially to the circumferential direction. Alternatively, the spring travel has an angle of more than 10°, but preferably of at least less than 45°. The compression spring is preferably arranged on a radial projection of the clamping element holder. The compression spring is preferably supported by the force transmission unit and / or the housing component. The design according to the invention allows the preload unit to be advantageously compact.

[0048] It is further proposed that at least one spring element, or another spring element, of the preload unit be designed as a sheet metal spring. The sheet metal spring preferably comprises a support body and a spring leaf projecting from the support body. The support body is designed, for example, analogous to a support body of the spring unit of the friction unit, on which, in particular, two spring elements of the spring unit are arranged. The support body is preferably attached to the clamping element holder, in particular overmolded by the clamping element holder, or formed integrally with it. The support body preferably has a principal plane of extension that is at least substantially parallel to the radial direction. The spring leaf is preferably arranged at an end of the support body facing away from the clamping element holder in the radial direction and extends from there towards the clamping element holder.The spring leaf is preferably arranged circumferentially between the support body and the power transmission element and / or the housing component. At one end facing the clamping element holder, the spring leaf preferably has a bend in the direction of the support body. Preferably, in at least one operating state of the drive device, the bend is designed to abut the power transmission element and / or the housing component. The design according to the invention advantageously allows the drive device to be easily assembled.

[0049] It is further proposed that the preloading unit and the friction unit be arranged on the same receiving area of ​​a clamping element holder of the control unit, in particular the aforementioned clamping element holder. Preferably, the clamping element holder has at least one mounting structure element on which the control unit and / or the preloading unit is arranged. The clamping element holder preferably comprises an annular base body in which a plurality of the receiving areas are arranged. The mounting structure element preferably extends radially away from the annular base body.The mounting structure element can be designed as a receptacle, in particular a bushing, as an extension, as a guide rail, as a weld surface, or as any other structure deemed useful by a person skilled in the art, in order to arrange, and in particular to fasten, the control unit and / or the preloading unit to the clamping element holder body. Preferably, the clamping element holder body comprises several, in particular identical, mounting structures, which are preferably arranged regularly, in particular rotationally symmetrically, in the circumferential direction on the annular base body. The mounting structure can extend circumferentially over exactly one or more receiving areas. The phrase "the preloading unit and the friction unit are arranged on the same receiving area" means, in particular, that they are arranged on the same mounting structure, regardless of how many receiving areas this mounting structure extends over.Preferably, the friction unit and / or the preload unit comprises several separate, identical assemblies, each with at least one spring element, distributed across the different mounting structures. Preferably, the friction unit and the preload unit each comprise at least one assembly arranged on the same mounting structure. Preferably, particularly in a preload unit configuration with compression springs, one assembly of the friction unit is arranged on each mounting structure. Preferably, particularly in a preload unit configuration with at least one compression spring, an additional assembly of the preload unit is arranged on at least one, and in particular each, of the mounting structures. The design according to the invention allows for an advantageously homogeneously distributed, and in particular rotationally symmetrical, force application to the clamping element base body.In particular, the risk of imbalance in the drive device can be advantageously kept low.

[0050] It is further proposed that the preload unit and the friction unit are arranged on different receiving areas of one, in particular the aforementioned, clamping element retaining body of the control unit. Preferably, especially in an embodiment of the preload unit with at least one sheet metal spring, either a friction unit assembly or a preload unit assembly is arranged on at least one, in particular each, mounting structure. In a specific embodiment, the preload unit comprises an assembly with a sheet metal spring on one of the mounting structures, on which, in particular, no mounting structure of the friction unit is arranged, and at least one assembly with a compression spring on at least one further of the mounting structures, on which a friction unit assembly is also arranged.The number of mounting structures with assemblies of the friction unit, and in particular without assemblies of the preload unit, and the number of mounting structures with assemblies of the preload unit, and in particular without assemblies of the friction unit, can be the same or different. The design according to the invention allows the drive device to be advantageously easy to mount.

[0051] Furthermore, a drive unit for an electric bicycle with a drive device according to the invention is proposed. The drive device is arranged, in particular, at least partially, and preferably at least predominantly, within the housing of the drive unit. Preferably, the electric motor and / or the gearbox are arranged at least predominantly within the housing. Advantageously, a particularly robust and / or durable drive unit can be provided. Advantageously, the drive unit can be operated with particular care.

[0052] Furthermore, an electric bicycle with a drive unit according to the invention is proposed. The drive unit, in particular the housing of the drive unit, is preferably attached to the frame of the electric bicycle. The electric bicycle preferably includes the wrap-around means. It is conceivable that at least the housing of the drive unit is formed at least partially integrally with at least a part of the frame. Advantageously, an electric bicycle with a particularly responsive bidirectional freewheel can be provided. Advantageously, particularly precise handling, especially drive behavior, can be achieved.

[0053] The drive device, drive unit, and / or electric bicycle according to the invention are not intended to be limited to the application and embodiment described above. In particular, the drive device, drive unit, and / or electric bicycle according to the invention may, in order to fulfill a function described herein, have a different number of individual elements, components, and units than the number specified herein. Furthermore, values ​​within the specified limits of the value ranges stated in this disclosure shall also be considered disclosed and freely usable. Drawings

[0054] Further advantages will become apparent from the following description of the drawings. The drawings illustrate two exemplary embodiments of the invention. The drawings, the description, and the claims contain numerous features in combination. A person skilled in the art will expediently consider the features individually and combine them into meaningful further combinations.

[0055] They show: Fig. 1 an electric bicycle according to the invention with a drive unit according to the invention in a schematic representation, Fig. 2 a simplified schematic representation of a drive device of the drive unit according to the invention, Fig. 3 the drive unit in a perspective sectional view, Fig. 4 the drive device in a perspective view, Fig. 5 the drive device in an exploded view, Fig. 6 a spring element of the drive device and Fig. 7 a section of a drive device according to the invention of an alternative embodiment in a schematic representation. Description of the exemplary implementations

[0056] Fig. Figure 1 shows an electric bicycle 14a. The electric bicycle 14a has a frame 68a. The electric bicycle 14a includes a drive unit 12a. The drive unit 12a is arranged on the frame 68a. The drive unit 12a is located in a bottom bracket area 70a of the electric bicycle 14a. The drive unit 12a includes a housing 72a (see Figure 1). Fig. 3) The drive unit 12a comprises an electric motor 74a. The drive unit 12a includes a gearbox 76a for transmitting a drive force from the drive unit 12a, in particular from the electric motor 74a, to an output pinion 108a of the drive unit 12a. The output pinion 108a is designed as a chainring or the like. The output pinion 108a is connected to a gearbox output of the gearbox 76a.

[0057] The drive unit 12a comprises at least one drive device 10a. The drive device 10a is arranged at least partially, preferably at least for the most part, within the housing 72a. Fig. Figure 2 shows a simplified diagram of the construction of the drive device 10a. The drive device 10a has a bidirectional freewheel 16a. The freewheel 16a is designed as a friction-based freewheel. The freewheel 16a differs from a pawl freewheel. The freewheel 16a has at least one clamping element unit 18a. The clamping element unit 18a is designed as a clamping roller unit. Alternatively, however, it is also conceivable that the clamping element unit 18a is designed as a clamping body unit or as a clamping ball unit. The clamping element unit 18a is arranged at the gearbox output of the drive unit 12a. Alternatively, it is also conceivable that the clamping element unit 18a is arranged at another position within the gearbox 76a.

[0058] The drive unit 12a comprises at least one crank shaft (not shown here). The crank shaft can be driven by a user via pedals. The output sprocket 108a is connected to the crank shaft in such a way that the output sprocket 108a can be driven by a rotation of the crank shaft, in particular at least in one direction of rotation, preferably in the direction of a forward rotation 78a of the drive device 10a. The forward rotation 78a corresponds to a forward movement of the electric bicycle 14a. It is conceivable that a shaft 50a is rotatably mounted to the crank shaft. Additionally, it is conceivable that the drive unit 12a has a further freewheel (not shown here) which is arranged between the shaft 50a and the crank shaft. The further freewheel is preferably designed to prevent the crank shaft from rotating when the shaft 50a is rotating.Alternatively, it is conceivable that the shaft 50a is rotationally fixed to the crank axle. In particular, it is also conceivable that the shaft 50a is formed integrally with the crank axle. Furthermore, it is also conceivable that the shaft 50a corresponds to the crank axle.

[0059] The drive device 10a comprises at least one power transmission element 42a for transmitting a drive force from the drive unit 12a. The clamping element unit 18a is arranged on the power transmission element 42a. The power transmission element 42a is designed as a spur gear. The spur gear has external teeth. It is conceivable that the external teeth are designed as spur gears or as helical gears. Alternatively, however, it is also conceivable that the power transmission element 42a is designed as a planet gear, a ring gear, a sun gear, or as another power transmission element 42a that would appear appropriate to a person skilled in the art. The power transmission element 42a forms the gearbox output of the drive unit 12a. Alternatively, however, it is also conceivable that the power transmission element 42a is arranged within the gearbox 76a and is intended, in particular, for power transmission to an intermediate shaft of the gearbox 76a.

[0060] The drive device 10a comprises at least the shaft 50a. The shaft 50a is designed as an output shaft. Alternatively, however, it is also conceivable that the shaft 50a is designed as an intermediate shaft, which is arranged in particular within the gearbox 76a, or the like. The output pinion 108a is rotationally fixed to the shaft 50a. It is conceivable that the output pinion 108a is formed integrally with the shaft 50a.

[0061] The freewheel 16a has a rotation axis 34a. The shaft 50a and the power transmission element 42a are arranged coaxially around the rotation axis 34a (see also Fig. 3, Fig. 4 and Fig. 5) The shaft 50a, the crank axle and / or the power transmission element 42a are / are rotatably mounted about the axis of rotation 34a. A torque can be generated at the output pinion 108a by rotating the shaft 50a about the axis of rotation 34a. The clamping element unit 18a is designed to interrupt the transmission of a motor torque directed forward with respect to the forward direction of the electric bicycle 14a to the shaft 50a, in particular the output pinion 108a, if the rotational speed of the shaft 50a is greater than the rotational speed of the power transmission element 42a driven by the motor torque.The clamping element unit 18a is configured to interrupt the transmission of a motor torque directed backwards with respect to the forward direction of the electric bicycle 14a to the shaft 50a, in particular the output pinion 108a, if the rotational speed of the shaft 50a, in particular of the output pinion 108a, is greater than the rotational speed of the power transmission element 42a driven by the motor torque. The clamping element unit 18a is configured to interrupt the transmission of a torque from the shaft 50a, in particular of the output pinion 108a, to the power transmission element 42a, preferably the gearbox 76a and / or the electric motor 74a, if the shaft 50a, in particular of the output pinion 108a, rotates backwards with respect to the forward direction of rotation 78a.The clamping element unit 18a is designed to interrupt the transmission of the torque of the shaft 50a, in particular of the output pinion 108a, from the shaft 50a, in particular of the output pinion 108a, to the power transmission element 42a, preferably to the gearbox 76a and / or the electric motor 74a, regardless of the speed of the power transmission element 42a and regardless of the speed of the shaft 50a, in particular of the output pinion 108a.

[0062] The clamping element unit 18a is designed to decouple vibrations of a wrapping element 58a. The wrapping element 58a is designed as a chain. Alternatively, it is also conceivable that the wrapping element 58a is designed as a belt or the like. The wrapping element 58a is preferably rotationally fixed to the output shaft, in particular the output pinion 108a. The wrapping element 58a is designed to transmit a drive force from the shaft 50a, in particular from the output pinion 108a, to a drive wheel 80a of the electric bicycle 14a. The drive wheel 80a is designed as a rear wheel of the electric bicycle 14a. Alternatively, however, it is also conceivable that the drive wheel 80a is designed as a front wheel of the electric bicycle 14a.The clamping element unit 18a is designed to counteract the transmission of vibrations from the wrapping element 58a to components of the drive unit 12a, which are located in the drive train downstream of the clamping element unit 18a, originating from the wrapping element 58a. The clamping element unit 18a is also designed to counteract the transmission of vibrations from the wrapping element 58a to the gearbox 76a and / or the electric motor 74a.

[0063] The clamping element unit 18a comprises a multitude of rolling elements 20a (in the simplified schematic representation in Fig. Figure 2 shows only one rolling element 20a). It is also conceivable that the clamping element unit 18a comprises only one rolling element 20a. The rolling elements 20a are designed as rollers. Alternatively, it is also conceivable that the rolling elements 20a are designed as spheres, barrels, needles, cones, or other bodies of revolution that would appear sensible to a person skilled in the art. The rolling elements 20a are provided in a clamping position for torque transmission between the power transmission element 42a and the shaft 50a. The rolling elements 20a are provided in a free-rotating position for interrupting torque transmission between the power transmission element 42a and the shaft 50a.

[0064] The clamping element unit 18a comprises at least one sleeve 40a. The sleeve 40a is arranged on the power transmission element 42a. The sleeve 40a is rotationally fixed to the power transmission element 42a. It is conceivable that the sleeve 40a is formed integrally with the power transmission element 42a. It is also conceivable that the sleeve 40a is formed by the power transmission element 42a. The rolling elements 20a are arranged between the power transmission element 42a, in particular the sleeve 40a, and the shaft 50a. The rolling elements 20a are arranged uniformly. The rolling elements 20a are arranged uniformly along a circumferential direction of the shaft 50a, which in particular runs in a plane perpendicular to the axis of rotation 34a.

[0065] The clamping element unit 18a has at least one clamping surface 82a, preferably a plurality of clamping surfaces 82a. The sleeve 40a has the at least one clamping surface 82a. The clamping surface 82a is designed to interact with at least one of the rolling elements 20a to transmit torque between the power transmission element 42a and the shaft 50a. The clamping element unit 18a has at least one further clamping surface 84a. The further clamping surface 84a is designed to interact with at least one of the rolling elements 20a to transmit torque between the power transmission element 42a and the shaft 50a. The shaft 50a has a cylindrical surface 86a. The further clamping surface 84a is formed by the cylindrical surface 86a of the shaft 50a. The sleeve 40a has an inner surface 88a. The inner surface 88a faces the shaft 50a. The inner surface 88a has at least one clamping surface 84.One number of clamping surfaces 82a corresponds to one number of rolling elements 20a. Each rolling element 20a is assigned one of the clamping surfaces 82a.

[0066] The rolling elements 20a are each designed to be clamped between the power transmission element 42a and the shaft 50a with one of the clamping surfaces 82a and the other clamping surfaces 84a for torque transmission. The sleeve 40a has at least a plurality of recesses 90a for arranging the rolling elements 20a (in the simplified schematic representation in Fig. Figure 2 shows only a recess 90a). A number of recesses 90a corresponds to a number of rolling elements 20a. One of the clamping surfaces 82a is arranged in each of the recesses 90a. The recesses 90a are asymmetrically designed, particularly at least in one circumferential direction of the force transmission element 42a, which preferably lies in a plane perpendicular to the axis of rotation 34a. The recesses 90a are designed such that the rolling elements 20a can be arranged in the recesses 90a in a clamping position on the clamping surface 82a and in a free-rotating position.

[0067] The clamping element unit 18a comprises at least one clamping element holding body 36a (in Fig. Figure 2 shows the clamping element holder 36a in a simplified schematic representation. The clamping element holder 36a has a plurality of receiving areas 92a for the rolling elements 20a. The clamping element holder 36a is ring-shaped (see also Figure 2). Fig. 4 and Fig. 5) The clamping element retaining body 36a is designed as a cage ring. The number of receiving areas 92a corresponds to the number of rolling elements 20a. The receiving areas 92a are separated from one another. The receiving areas 92a limit the movement of the rolling elements 20a, in particular about the axis of rotation 34a, preferably in the circumferential direction, relative to the clamping element retaining body 36a. The clamping element retaining body 36a is arranged between the shaft 50a and the force transmission element 42a, in particular the sleeve 40a. The clamping element retaining body 36a is movably arranged relative to the force transmission element 42a, in particular the sleeve 40a, and / or the shaft 50a. The clamping element retaining body 36a is designed to guide the rolling elements 20a.

[0068] The clamping element unit 18a comprises a mechanical control unit 22a. The control unit 22a is designed to switch between a freewheel state and a torque transmission state of the freewheel 16a. The freewheel state is a state of the freewheel 16a in which torque transmission between the power transmission element 42a and the shaft 50a is interrupted. The torque transmission state is a state of the freewheel 16a in which torque transmission occurs between the power transmission element 42a and the shaft 50a. Switching between the freewheel state and the torque transmission state is performed automatically by the control unit 22a, specifically without user intervention and / or without electronic control. The control unit 22a is free of electrical components. Alternatively, however, it is also conceivable that the clamping element unit 18a includes an electronic control unit.

[0069] The control unit 22a has a friction unit 24a, which is designed to generate an actuating force. The friction unit 24a is designed to move the clamping element retaining body 36a relative to the power transmission element 42a and / or the shaft 50a, in particular to rotate it about the axis of rotation 34a. The friction unit 24a is designed, at least, to release a torque transmission state of the freewheel 16a, depending on a relative movement of the power transmission element 42a to the shaft 50a. The friction unit 24a is designed, at least, to switch the freewheel 16a from the torque transmission state to the freewheel state of the freewheel 16a, depending on a relative movement of the power transmission element 42a to the shaft 50a, by means of the actuating force.The friction unit 24a is designed to position the rolling elements 20a relative to the power transmission element 42a, in particular the sleeve 40a, and / or the shaft 50a, preferably to switch the freewheel 16a, preferably at least from the torque transmission state to the freewheel state.

[0070] The friction unit 24a is designed to generate a frictional force between the clamping element retaining body 36a and a friction element 94a that is separate from the clamping element retaining body 36a. The friction element 94a is a stationary component of the freewheel 16a. The friction element 94a is designed as a friction ring. The friction element 94a is rotationally fixed to a housing component 62a of the housing 72a. Alternatively, it is also conceivable that the friction element 94a is formed by a stationary component of the electric bicycle 14a, in particular the drive unit 12a. The friction element 94a is alternatively formed, for example, by the housing component 62a, by a frame element of the frame 68a, or the like. The friction unit 24a forms a frictional contact between the clamping element retaining body 36a and the friction element 94a. The friction unit 24a has a plurality of friction elements 66a (in the simplified schematic representation in Fig. (Figure 2 shows only two friction elements 66a). The friction unit 24a has four friction elements 66a. Alternatively, it is also conceivable that the friction unit 24a has a number of friction elements 66a other than four, for example, one friction element 66a, two friction elements 66a, three friction elements 66a, or more than four friction elements 66a. The friction elements 66a are provided to form the frictional contact between the clamping element holding body 36a and the friction body 94a. The friction elements 66a are arranged in the circumferential direction of the clamping element holding body 36a, which runs in a plane perpendicular to the axis of rotation 34a.

[0071] The friction elements 66a each have two friction surfaces 38a for forming the frictional contact between the clamping element holder 36a and the friction body 94a. Alternatively, it is also conceivable that the friction elements 66a each have only one friction surface 38a or more than two friction surfaces 38a. Alternatively, it is also conceivable that the friction elements 66a are arranged unevenly in the circumferential direction, preferably on the clamping element holder 36a or the friction body 94a. The friction elements 66a are attached to the clamping element holder 36a. The friction elements 66a are formed integrally with the clamping element holder 36a.

[0072] The actuating force is a frictional force. The friction unit 24a is designed to generate the actuating force in at least one operating state of the freewheel 16a through static and / or sliding friction between the clamping element holder 36a and the friction body 94a. The actuating force, in particular the frictional force, acts against a torque applied to the clamping element holder 36a, at least in the operating state of the freewheel 16a. The actuating force, preferably the frictional force, is designed to delay rotation of the clamping element holder 36a about the axis of rotation 34a relative to the shaft 50a, particularly at least in the freewheel state.

[0073] The drive device 10a comprises at least one bearing unit 96a (see Fig. 3), which is arranged at least partially between the power transmission element 42a, in particular the sleeve 40a, and the shaft 50a. The bearing unit 96a is designed to mount the power transmission element 42a and the shaft 50a rotatably relative to each other and / or at a fixed radial distance from each other. The bearing unit 96a comprises at least two bearing elements 54a. Alternatively, it is also conceivable that the bearing unit 96a comprises only one bearing element 54a or more than two bearing elements 54a. The bearing elements 54a are designed as sliding bearing rings. The bearing elements 54a are arranged between the power transmission element 42a, in particular the sleeve 40a, and the shaft 50a.

[0074] The clamping element unit 18a is designed to clamp the rolling elements 20a in the recesses 90a by means of the respective clamping surface 82a when the rotational speed of the power transmission element 42a in the forward direction 78a is greater than or equal to the rotational speed of the shaft 50a. When the power transmission element 42a rotates in the forward direction 78a, and its rotational speed is greater than that of the shaft 50a, the friction unit 24a is designed to brake the clamping element retaining body 36a relative to the power transmission element 42a by means of the actuating force, in particular the frictional force, in order to bring the rolling elements 20a into contact with the clamping surfaces 82a in the recesses 90a of the sleeve 40a and clamp them.The clamping element unit 18a is designed to generate a force on the rolling elements 20a via the actuating force, in particular the frictional force, when the shaft 50a rotates in a reverse direction relative to the forward direction of rotation 78a, in order to release the rolling elements 20a from the clamping surfaces 82a, so that the freewheel 16a is switched to the freewheeling state. The actuating force, in particular the frictional force, can cause the rolling elements 20a to clamp with the power transmission element 42a, in particular the sleeve 40a, and the shaft 50a if the rotational speed of the power transmission element 42a is greater than the rotational speed of the shaft 50a, preferably at least when the power transmission element 42a rotates forward relative to the forward direction of rotation 78a.By clamping the rolling elements 20a with the power transmission element 42a, in particular the sleeve 40a, and the shaft 50a, a torque can be transmitted between the power transmission element 42a and the shaft 50a.

[0075] The rolling elements 20a are rotationally fixed to the power transmission element 42a, in particular the sleeve 40a, and the shaft 50a in the torque transmission state. The rolling elements 20a are in the clamping position, in particular, when the freewheel 16a is in the torque transmission state. In the freewheel state, the rolling elements 20a are arranged to rotate freely in the recesses 90a. The rolling elements 20a are in the free-rotating position, in particular, when the freewheel 16a is in the freewheel state. The rolling elements 20a are arranged to rotate freely in the recesses 90a when the shaft 50a rotates backward with respect to the forward direction of rotation 78a. The rolling elements 20a are arranged to rotate freely in the recesses 90a when the shaft 50a rotates forward with respect to the forward direction of rotation 78a and the rotational speed of the shaft 50a is greater than the rotational speed of the power transmission element 42a.The rolling elements 20a are arranged to rotate freely in the recesses 90a when the power transmission element 42a rotates backwards with respect to the forward direction of rotation 78a. The clamping element unit 18a is designed to release the rolling elements 20a from the clamping by means of the clamping element retaining body 36a when the rotational speed of the shaft 50a is greater than the rotational speed of the power transmission element 42a.

[0076] The clamping element unit 18a comprises at least one preload unit 112a, which is designed to generate a preload force. The control unit 22a comprises the at least one preload unit 112a in addition to the friction unit 24a. The friction unit 24a and the preload unit 112a are arranged such that a direction of actuation of the friction unit 24a and a direction of action of the preload force are preferably oriented transversely, and in particular at least substantially perpendicularly, to each other. The preload unit 112a is preferably arranged on the clamping element holding body 36a. The preload unit 112a is, for example, arranged on the force transmission element 42a. The preload unit 112a preferably comprises at least one spring element 114a, which acts on the clamping element holding body 36a to exert a spring force in or against the forward direction of rotation 78a.The spring element 114a engages the clamping element retaining body 36a in the circumferential direction, preferably on a side facing the recess 90a, and in particular on a side facing away from the clamping surface 82a of the sleeve 40a.

[0077] The friction unit 24a comprises at least one spring unit 26a. The clamping element retaining body 36a is connected to the friction body 94a via the spring unit 26a. The spring unit 26a is designed to generate a holding force between the clamping element retaining body 36a and the friction body 94a. The spring unit 26a is designed to generate the actuating force, in particular the frictional force, of the friction unit 24a. The spring unit 26a has four spring elements 32a (see figure). Fig. 4 and Fig. 5) Alternatively, it is also conceivable that the spring unit 26a has a number of spring elements 32a other than four, for example, only one spring element 32a, two spring elements 32a, three spring elements 32a, or more than four spring elements 32a. The friction elements 66a are formed by the spring elements 32a. The spring elements 32a are designed as bending springs 28a. Alternatively, it is also conceivable that the spring elements 32a are designed as torsion springs, disc springs, volute springs, ring springs, or the like. Furthermore, it is also conceivable that the spring elements 32a are designed as rubber-elastic elements. The spring elements 32a are arranged on the clamping element holding body 36a. The spring elements 32a are arranged between the clamping element holding body 36a and the friction body 94a. The clamping element retaining body 36a is connected to the friction body 94a via the spring elements 32a.The four spring elements 32a each have two mounting ramps 60a (see . Fig. 6) The mounting ramps 60a are formed by surfaces angled to the axis of rotation 34a, preferably running at a different direction than perpendicular.

[0078] The bending springs 28a are designed as leaf springs 30a. Alternatively, it is also conceivable that the bending springs 28a are designed as wire springs, needle springs, torsion springs, or the like. Preferably, the spring unit 26a is designed without helical springs. The leaf springs 30a are designed as at least two-leaf leaf springs. Alternatively, however, it is also conceivable that the leaf springs 30a are designed as single-leaf leaf springs, as coil springs, as impact springs, as elliptical springs, as parabolic springs, as wave springs, or as other leaf springs 30a that would appear useful to a person skilled in the art. The leaf springs 30a each have two spring leaves 56a (see Figure 1). Fig. 6) The friction surfaces 38a of the friction elements 66a are each arranged on the spring wings 56a.

[0079] The rolling elements 20a are arranged spring-free on the clamping element holder 36a. The receiving areas 92a for the rolling elements 20a are free of spring elements. In particular, an area between the rolling elements 20a and the clamping element holder 36a, preferably at least in the respective receiving area 92a, is free of spring elements. The rolling elements 20a are not supported on the clamping element holder 36a by means of spring elements.

[0080] The spring elements 32a are attached to the clamping element holder 36a. The spring elements 32a are made of a material different from the material of the clamping element holder 36a. The spring elements 32a are made of metal. Alternatively, however, it is also conceivable that the spring elements 32a are made of plastic or another material that would appear suitable to a person skilled in the art. The clamping element holder 36a is made of plastic. Alternatively, however, it is also conceivable that the clamping element holder 36a is made of metal or another material that would appear suitable to a person skilled in the art. Alternatively, however, it is also conceivable that the spring elements 32a and the clamping element holder 36a are made of the same material.

[0081] The spring elements 32a are formed integrally with the clamping element holder 36a. The spring elements 32a are overmolded by the clamping element holder 36a. The spring elements 32a are at least partially overmolded by the clamping element holder 36a.

[0082] The spring elements 32a each have two connecting elements 106a for connecting them to the clamping element holder 36a. The connecting elements 106a are designed as openings. Alternatively, however, it is also conceivable that the connecting elements 106a are designed as other connecting elements 106a that would appear useful to a person skilled in the art. The connecting elements 106a are intended to be injection-molded through the clamping element holder 36a during the manufacture of the clamping element unit 18a. The spring elements 32a each have a mounting element 104a. The respective mounting element 104a is intended to support the arrangement of the spring elements 32a on the clamping element holder 36a in an assembly position prior to overmolding. The mounting elements 104a are designed as openings.Alternatively, it is also conceivable that the mounting elements 104a are designed as projections or as other mounting elements 104a that would appear useful to a specialist.

[0083] The friction surfaces 38a of the friction unit 24a, in particular the friction elements 66a, extend in the axial direction. The axial direction runs parallel to the axis of rotation 34a. The friction surfaces 38a are at least partially curved. Alternatively or additionally, it is conceivable that the friction surfaces 38a extend at least partially in a straight line. The friction surfaces 38a each have a principal plane of extension, which runs at least substantially parallel to the axial direction.

[0084] The axially extending friction surfaces 38a are arranged on a side facing away from the clamping element holding body 36a when viewed in the axial direction. The spring wings 56a of the spring elements 32a are arranged on the side facing away from the clamping element holding body 36a, particularly when viewed at least in the axial direction. The axially extending friction surfaces 38a are oriented inwards when viewed in the radial direction.

[0085] The friction surfaces 38a are arranged facing the shaft 50a. The friction surfaces 38a are arranged facing the axis of rotation 34a.

[0086] The force transmission element 42a has four through-holes 44a, through each of which a mounting structure of the clamping element retaining body 36a is guided at least partially outwards in a radial direction. Alternatively, the force transmission element 42a may have a number of through-holes 44a other than four, for example, only one through-hole 44a, two, three, or more than four through-holes 44a. A number of through-holes 44a corresponds in particular to a number of friction elements 66a, especially spring elements 32a. However, it is also conceivable that the number of through-holes 44a differs from the number of friction elements 66a, especially spring elements 32a.

[0087] The mounting structure of the clamping element holder 36a is designed, for example, as a receptacle that accommodates one of the spring elements 32a of the spring unit 26a. The mounting structure is manufactured, in particular, by overmolding the spring element 32a. The preload unit 112a and the friction unit 24a are arranged on the same mounting structure of the clamping element holder 36a. Specifically, at least one spring element 32a of the friction unit 24a and one spring element 114a, 116a of the preload unit 112a are arranged on each mounting structure of the clamping element holder 36a. The preload unit 112a preferably comprises at least one, in particular exactly one, and here by way of example four, spring elements 114a, 116a per through-hole 44a, two of which are designated with a reference numeral. The spring elements 114a, 116a of the preload unit 112a are designed as compression springs.The spring elements 114a, 116a are arranged by way of example in the feedthroughs 44a and are supported in particular by one wall each that bounds the feedthroughs 44a in the circumferential direction. The spring elements 114a, 116a engage the clamping element retaining body 36a in the circumferential direction, preferably at one of the mounting structures each.

[0088] The maximum diameter 46a of the rolling elements 20a is between 6% and 20% of the maximum inner diameter 48a of the force transmission element 42a, in particular the sleeve 40a. Preferably, the maximum diameter 46a of the rolling elements 20a is at most 15%, more preferably at most 10%, of the maximum inner diameter 48a of the force transmission element 42a, in particular the sleeve 40a. Alternatively, it is also conceivable that the maximum diameter 46a of the rolling elements 20a is outside the range of 6% to 20% of the maximum inner diameter 48a of the force transmission element 42a, in particular the sleeve 40a. The inner diameter 48a is measured in the radial direction. Preferably, the maximum diameter 46a is measured in the radial direction.The maximum diameter 46a of the rolling elements 20a is between 8% and 25% of the maximum diameter 52a of the shaft 50a. Preferably, the maximum diameter 46a of the rolling elements 20a is at most 15%, and more preferably at most 12%, of the maximum diameter 52a of the shaft 50a. Alternatively, it is also conceivable that the maximum diameter 46a of the rolling elements 20a is outside the range of 8% to 25% of the maximum diameter 52a of the shaft 50a. In particular, the maximum diameter 52a of the shaft 50a is measured in the radial direction.

[0089] The maximum diameter 52a of the shaft 50a is, for example, a maximum of 38 mm; a maximum diameter 52a of the shaft 50a is particularly preferably 32 mm. The maximum inner diameter 48a of the power transmission element 42a, in particular the sleeve 40a, is a maximum of 45 mm. Preferably, the maximum inner diameter 48a of the power transmission element 42a, in particular the sleeve 40a, is between 40 mm and 41 mm. Alternatively, however, it is also conceivable that the maximum inner diameter 48a of the power transmission element 42a, in particular the sleeve 40a, is greater than 45 mm. The maximum diameter 46a of the rolling elements 20a is a maximum of 5 mm. Preferably, the maximum diameter 46a of the rolling elements 20a is substantially 3.5 mm. Alternatively, it is also conceivable that the maximum diameter 46a of the rolling elements 20a is greater than 5 mm.

[0090] The maximum angle of movement, in particular the translation angle, of the rolling element 20a relative to the clamping element holder 36a about the axis of rotation 34a of the freewheel 16a is a maximum of 1.5°. Preferably, the maximum angle of movement, in particular the translation angle, of the rolling element 20a relative to the clamping element holder 36a is between 0° and 1°. Particularly preferably, the maximum angle of movement, in particular the translation angle, of the rolling element 20a relative to the clamping element holder 36a is substantially 0.5°. Alternatively, however, it is also conceivable that the maximum angle of movement, in particular the translation angle, of the rolling element 20a relative to the clamping element holder 36a about the axis of rotation 34a is greater than 1.5°.

[0091] The maximum angle between the respective clamping position of the rolling elements 20a and the respective maximum free rotation position of the rolling elements 20a about the axis of rotation 34a of the freewheel 16a is a maximum of 5°. Preferably, the maximum angle between the respective clamping position of the rolling elements 20a and the respective maximum free rotation position of the rolling elements 20a about the axis of rotation 34a of the freewheel 16a is a maximum of 2.5°. Preferably, the maximum angle between the respective clamping position of the rolling elements 20a and the respective maximum free rotation position of the rolling elements 20a about the axis of rotation 34a of the freewheel 16a is between 0.3° and 2.5°, particularly preferably between 0.4° and 2°. Most preferably, the maximum angle between the respective clamping position of the rolling elements 20a and the respective maximum free rotation position of the rolling elements 20a about the axis of rotation 34a is at least substantially 0.8°.The respective maximum free rotation position and the respective clamping position of the rolling elements 20a are each located in one of the recesses 90a for the rolling elements 20a. The respective maximum free rotation position and the clamping position are located at opposite end regions of the recesses 90a. The clamping surfaces 82a are each arranged on a rear side of the recesses 90a with respect to the forward direction of rotation 78a. The respective free rotation position is arranged on a front side of the recesses 90a with respect to the forward direction of rotation 78a. The recesses 90a have a stop for the respective rolling element 20a in the respective end region where, in particular, the free rotation position of the respective rolling element 20a is located. Alternatively, it is also conceivable that the maximum angle between the respective clamping position and the respective maximum free rotation position of the rolling elements 20a about the axis of rotation 34a of the freewheel 16a is greater than 5°.The rolling elements 20a are each in the maximum free rotation position when the rolling elements 20a are in contact with the respective stop of the recesses 90a.

[0092] The clamping element unit 18a and the force transmission element 42a have a common plane of intersection, which is at least substantially perpendicular to the axis of rotation 34a. The clamping element unit 18a is arranged at least substantially completely within the force transmission element 42a. Alternatively, it is also conceivable that the clamping element unit 18a is arranged axially offset from the force transmission element 42a such that at least the external teeth of the force transmission element 42a and the clamping element unit 18a are free from a common plane of intersection, which is at least substantially perpendicular to the axis of rotation 34a.

[0093] The sum of a cage angle and a spring angle is less than or equal to a sleeve clearance angle. The clamping element retaining body angle is formed by the sum of a clamping element retaining body clearance angle and a clamping element retaining body load angle. The clamping element retaining body angle is a maximum of 2.5°. Particularly preferably, the clamping element retaining body angle is substantially 1.8°. Alternatively, however, it is also conceivable that the clamping element retaining body angle is greater than 2.5°. The clamping element retaining body clearance angle corresponds to the respective maximum angle of movement, in particular translation angle, of the rolling elements 20a relative to the clamping element retaining body 36a about the axis of rotation 34a of the freewheel 16a. The clamping element retaining body load angle is the sum of a mechanical clamping element retaining body load angle and a chemical and / or thermal clamping element retaining body load angle.The clamping element holding body load angle is a maximum of 1°. Particularly preferably, the clamping element holding body load angle is substantially 0.8°. Alternatively, however, it is also conceivable that the clamping element holding body load angle is greater than 1°. The mechanical clamping element holding body load angle depends in particular on possible mechanical deformations of the clamping element holding body 36a during operation of the clamping element unit 18a. The mechanical clamping element holding body load angle is a maximum of 0.7°. Particularly preferably, the mechanical clamping element holding body load angle is substantially 0.5°. Alternatively, however, it is also conceivable that a value of the mechanical clamping element holding body load angle is greater than 0.7°.The chemical and / or thermal clamping element holding body load angle depends in particular on the clamping element holding body 36a with respect to possible thermal expansion, possible swelling of the material, for example due to moisture absorption, or the like. The chemical and / or thermal clamping element holding body load angle is a maximum of 0.5°. Particularly preferably, the chemical and / or thermal clamping element holding body load angle is substantially 0.3°. Alternatively, however, it is also conceivable that a value of the chemical and / or thermal clamping element holding body load angle is greater than 0.5°.

[0094] The sleeve clearance angle preferably corresponds to the respective maximum angle between the respective clamping position of the rolling elements 20a and the respective maximum free rotation position of the rolling elements 20a. The sum of the sleeve clearance angle and a sleeve load angle yields, in particular, a sleeve angle. The sleeve angle is a maximum of 6.5°, preferably a maximum of 3.5°. Most preferably, the sleeve angle is substantially 3.3°. Alternatively, however, it is also conceivable that the sleeve angle is greater than 6.5°. The sleeve load angle is preferably dependent at least on a possible deformation and / or expansion of the force transmission element 42a, in particular the sleeve 40a, preferably the clamping surfaces 82a, during operation of the clamping element unit 18a. The sleeve load angle is a maximum of 4°, preferably a maximum of 2°. Most preferably, the sleeve load angle is at least substantially 2.5°.Alternatively, it is also conceivable that the sleeve load angle has a value greater than 4°. The spring angle is, in particular, the sum of a spring clearance angle and a spring load angle. The spring angle is a maximum of 0.1°. Particularly preferably, the spring angle is substantially 0.05°. Alternatively, however, it is also conceivable that the spring angle is greater than 0.1°. The spring clearance angle refers in particular to any possible play in the connection between the clamping element retaining body 36a and the spring unit 26a, especially the spring elements 32a. The spring load angle depends in particular on any possible bending of the respective spring elements 32a. The spring load angle is preferably a maximum of 0.1°. Particularly preferably, the spring load angle is substantially 0.05°. Alternatively, however, it is also conceivable that the spring load angle is greater than 1°.A freewheel function angle is, in particular, a sum of the sleeve angle, the clamping element holding body angle, and the spring angle.

[0095] In the Fig. Figure 7 shows a further embodiment of the invention. The following descriptions and drawings are essentially limited to the differences between the embodiments, whereby, with regard to identically designated components, in particular components with the same reference numerals, reference is also generally made to the drawings and / or the description of the other embodiments, in particular the Fig. 1 to 6, reference can be made. To distinguish the embodiments, the letter a is the reference numeral of the embodiment in the Fig. 1 to 6 followed. In the exemplary embodiment of the Fig. In 7, the letter a is replaced by the letter b.

[0096] Fig. Figure 7 shows a drive device 10b for a drive unit (not shown here) of an electric bicycle (not shown here). The drive device 10b has a bidirectional freewheel 16b. The freewheel 16b has at least one clamping element unit 18b. The clamping element unit 18b comprises at least one mechanical control unit 22b. The control unit 22b has at least one friction unit 24b, which is provided for generating an actuating force. The friction unit 24b has at least one spring unit 26b. The freewheel 16b has at least one friction element 94b. The drive device 10b comprises at least one power transmission element 42b for transmitting a drive force from the drive unit.The spring unit 26b comprises at least one spring element 32b, which is attached to a mounting structure of a clamping element holding body 36b of the clamping element unit 18b, which projects into a passage 44b of the force transmission element 42b, in particular through it.

[0097] The clamping element unit 18b comprises at least one preload unit 112b, which is designed to generate a preload force. The preload unit 112b comprises at least one spring element 114b, 116b, which is designed as a sheet metal spring. The at least one sheet metal spring is preferably arranged on a further mounting structure of the clamping element holding body 36b, which projects into a further passage 44b' of the force transmission element 42b, and in particular projects through it. The sheet metal spring preferably comprises a support body 120b and a spring leaf 122b. The support body 120b is preferably attached to the further mounting structure. The support body 120b is preferably designed analogously to a support body of the spring element 32b, in particular with connecting elements as shown in Fig. 6 is shown (see connecting elements 106a of the Fig.6) The spring leaf 122b preferably extends from an end facing away from the clamping element holder 36b through the further passage 44b' in the direction of the clamping element holder 36b. A bend in the spring leaf 122b is preferably provided so that, in at least one operating state of the drive device 10b, it abuts a wall of the power transmission element 42b that limits the further passage 44b'.

[0098] Preferably, no spring element of the friction unit 24b is arranged on the further mounting structure to which the sheet metal spring is attached. The clamping element holding body 36b preferably comprises several, here for example four, mounting structures, each of which is equipped either with one of the spring elements 32b of the friction unit 24b or with one of the sheet metal springs of the preload unit 112b. The number of sheet metal springs and spring elements 32b of the friction unit 24b can be the same, as shown here with two of each, or different, for example in the ratio 3:1 or 1:3. The distribution of the spring elements 32b and the sheet metal springs can be rotationally symmetrical with respect to an axis of rotation 34b of the drive device 10b or irregular. In addition to the sheet metal springs, the preload unit 112b can have compression springs that act on the mounting structure to which the spring elements 32b of the friction unit 24b are attached.

Claims

[1] Drive device (10a; 10b) for a drive unit (12a; 12b) of an electric bicycle (14a; 14b), with a bidirectional freewheel (16a; 16b), wherein the freewheel (16a; 16b) comprises at least one clamping element unit (18a; 18b), characterized by that the clamping element unit (18a; 18b) comprises at least one pretensioning unit (112a; 112b) which is provided for generating a pretensioning force. [2] Drive device (10a; 10b) according to claim 1 characterized by that the clamping element unit (18a; 18b) comprises at least one mechanical control unit (22a; 22b), wherein the control unit (22a; 22b) comprises a friction unit (24a; 24b) which is provided for generating an actuating force, and wherein the control unit (22a; 22b) comprises the at least one pretensioning unit (112a; 112b). [3] Drive device (10a; 10b) according to claim 2, characterized bythat the friction unit (24a; 24b) and the pretensioning unit (112a; 112b) are arranged such that an adjusting direction of the friction unit (24a; 24b) and an effective direction of the pretensioning force are preferably aligned transversely, in particular at least substantially perpendicularly, to one another. [4] Drive device (10a; 10b) according to one of the preceding claims, characterized by that the pretensioning unit (112a; 112b) has at least one spring element (114a, 116a; 114b, 116b). [5] Drive device (10a) according to claim 4, characterized by that the at least one spring element (114a, 116a) is designed as a compression spring. [6] Drive device (10b) according to claim 4 or 5, characterized by that the at least one spring element (114b, 116b) or a further spring element of the pretensioning unit (112b) is designed as a sheet metal spring. [7] Drive device (10a) according to one of claims 2 to 6, characterized bythat the pretensioning unit (112a) and the friction unit (24a) are arranged on the same receiving area (92a) of a clamping element holding body (36a) of the control unit (22a). [8] Drive device (10b) according to one of claims 2 to 6, characterized by that the pretensioning unit (112b) and the friction unit (24b) are arranged on different receiving areas (92b) of a clamping element holding body (36b) of the control unit (22b). [9] Drive unit (12a; 12b) for an electric bicycle (14a; 14b) with a drive device (10a; 10b) according to one of the preceding claims. [10] Electric bicycle (14a; 14b) with a drive unit (12a; 12b) according to claim 9.

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