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

Abstract

The invention relates to a drive device (10a-10h) for a drive unit (12a-12h) of an electric bike (14a-14h), having a bidirectional freewheel (16a-16h). According to the invention, the freewheel (16a-16h) comprises at least one clamping element unit (18a-18h).

Description

[0001] Description

[0002] Drive device for a drive unit of an electric bicycle, drive unit and electric bicycle

[0003] State of the art

[0004] A drive device for a drive unit of an electric bicycle, with a bidirectional freewheel, has already been proposed.

[0005] Disclosure of the invention

[0006] The invention relates to a drive device for a drive unit of an electric bicycle, with a bidirectional freewheel.

[0007] It is proposed that the freewheel comprise at least one clamping element unit. The freewheel is preferably designed as a friction-locked freewheel. The clamping element unit is preferably designed as a clamping body unit, as a clamping ball unit, or as a clamping roller unit. In particular, the freewheel is designed differently from a pawl freewheel. The drive unit preferably comprises an electric motor. The drive unit in particular comprises a gear for transmitting a drive force of the drive unit to an output pinion of the drive unit. The output pinion is designed, for example, as a chainring or the like. The output pinion is preferably connected to a gear output of the gear. The clamping element unit is preferably arranged on the gear output of the drive unit. Alternatively, it is also conceivable for the clamping element unit to be arranged at a different position within the gear.Alternatively, the drive device can also be used on a vehicle other than an electric bicycle. It is conceivable that the vehicle comprises an internal combustion engine, an electric motor, or the like.

[0008] The drive device preferably comprises at least one power transmission element for transmitting a drive force of the drive unit. The clamping element unit is preferably arranged on the power transmission element. The power transmission element can be designed, for example, as a spur gear, a planetary gear, a ring gear, a sun gear, or as another power transmission element that appears appropriate to a person skilled in the art. Preferably, the power transmission element forms the transmission output of the drive unit. Alternatively, however, it is also conceivable for the power transmission element to be arranged within the transmission and, in particular, to be provided for power transmission to an intermediate shaft of the transmission. The drive device preferably comprises at least one shaft. The shaft is preferably designed as an output shaft.Alternatively, however, it is also conceivable for the shaft to be designed as an intermediate shaft, which is arranged in particular within the transmission, or the like. Preferably, the output pinion is connected in a rotationally fixed manner to the shaft designed as the output shaft. It is conceivable for the output pinion to be formed integrally with the output shaft. “Integral” can be understood to mean at least materially connected, for example by a welding process, an adhesive process, an injection molding process and / or another process that appears appropriate to a person skilled in the art, and / or advantageously formed in one piece, for example by production from a single casting and / or by production using a single or multi-component injection molding process and advantageously from a single blank.

[0009] The drive unit preferably comprises at least one pedal crankshaft. The pedal crankshaft can preferably be driven by a user via pedals. The drive device in particular has a forward direction of rotation, which corresponds in particular to a forward movement of the electric bicycle. The output pinion is preferably connected to the pedal crankshaft in such a way that the output pinion can be driven by a rotation of the pedal crankshaft, 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 and connected to the pedal crankshaft. In addition, it is conceivable that the drive unit has a further freewheel, which is arranged between the shaft and the pedal crankshaft. The further freewheel is preferably provided to prevent the pedal crankshaft from rotating when the shaft is rotating.Alternatively, it is conceivable for the shaft to be connected to the pedal crankshaft in a rotationally fixed manner. In particular, it is conceivable for the shaft to be formed integrally with the pedal crankshaft. Furthermore, it is conceivable for the shaft to correspond to the pedal crankshaft. Preferably, the shaft and the power transmission element are arranged coaxially with a rotational axis of the freewheel. In particular, the shaft, the pedal crankshaft, and / or the power transmission element are / are mounted for rotation about the rotational axis.

[0010] The clamping element unit is preferably configured to interrupt the transmission of a forward-directed motor torque relative to the forward direction of the electric bicycle to the shaft, in particular the output pinion, when a rotational speed of the shaft is greater than a 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 backward-directed motor torque relative to the forward direction of the electric bicycle to the shaft, in particular the output pinion, when 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, in particular the output pinion, to the power transmission element, preferably the transmission and / or the electric motor, when the shaft, in particular the output pinion, rotates backward relative to the forward direction of rotation, in particular the forward direction of the electric bicycle. The clamping element unit is preferably configured to interrupt the transmission of torque from the shaft, in particular the output pinion, to the power transmission element, preferably to the transmission and / or the electric motor, regardless of the rotational speed of the power transmission element and regardless of the rotational speed of the shaft, in particular the output pinion. The clamping element unit preferably comprises at least one clamping element.The clamping element is preferably provided in a clamped state of the clamping element, in particular between the force transmission element and the shaft, for torque transmission between the force transmission element and the shaft. The at least one clamping element is preferably provided in a state of the clamping element decoupled from the force transmission element and / or the shaft, in particular in a freely rotating state and / or spaced apart from the force transmission element and / or the shaft, for interrupting torque transmission between the force transmission element and the shaft. The clamping element is designed, for example, as a rolling element, as a, for example, non-circular, clamping body or the like. The clamping element is preferably designed 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.

[0011] The inventive design of the drive device advantageously makes it possible to provide a particularly responsive bidirectional freewheel for a drive unit of an electric bicycle. A particularly quiet bidirectional freewheel for a drive unit of an electric bicycle can advantageously be realized. The drive device advantageously makes it possible to realize particularly gentle operation of a drive unit, in particular a transmission and / or an electric motor. Advantageously, an undesired torque transmission from the shaft to the power transmission element can be counteracted by a movement of the shaft in any direction of rotation. Advantageously, a transmission of undesired torque from an output side to the electric motor and / or at least part of the transmission can be counteracted.

[0012] It is further proposed that the clamping element unit be provided for decoupling vibrations of a belt. The belt is designed, for example, as a chain, a belt, or the like. The belt is preferably connected in a rotationally fixed manner to the output shaft, in particular to the output pinion. The belt is provided, in particular, to transmit a drive force from the shaft, preferably designed as an output shaft, in particular from the output pinion, to a drive wheel of the electric bicycle. The drive wheel is preferably designed as a rear wheel of the electric bicycle. Alternatively, however, it is also conceivable for the drive wheel to be designed as a front wheel of the electric bicycle.The clamping element unit is preferably provided to counteract the transmission of vibrations of the belt means to components of the drive unit which, starting from the belt means, are arranged behind the clamping element unit in the drive train. The clamping element unit is preferably provided to counteract the transmission of vibrations of the belt means to the transmission and / or the electric motor. Particularly gentle operation can advantageously be ensured. Advantageously, the use of the clamping element unit can provide a particularly durable drive device, preferably a drive unit, in particular a particularly durable electric motor and / or a particularly durable transmission. Advantageously, gear rattle can be counteracted. Advantageously, the decoupling of vibrations of a belt means can be carried out with particularly low noise.

[0013] It is further proposed that the clamping element unit comprise at least one rolling body, in particular a roller. Alternatively, it is also conceivable for the rolling body to be designed as a sphere, a barrel, a needle, a cone, or any other rotating body that would appear appropriate to a person skilled in the art. The rolling body is preferably rotationally symmetrical. The at least one rolling body is preferably provided, in a clamped state of the rolling body, for torque transmission between the power transmission element and the shaft. The at least one rolling body is preferably provided, in a freely rotating state of the rolling body, for interrupting torque transmission between the power transmission element and the shaft. The clamping element unit preferably comprises a plurality of rolling bodies, in particular at least two, preferably at least three rolling bodies.The clamping element unit comprises, for example, at least one sleeve, which is arranged in particular on the force transmission element. The sleeve is preferably connected to the force transmission element in a rotationally fixed manner. The sleeve is preferably formed integrally with the force transmission element. It is also conceivable for the sleeve to be formed by the force transmission element. The at least one rolling element is arranged in particular between the force transmission element, in particular the sleeve, and the shaft.The rolling elements are preferably arranged uniformly. Preferably, a plurality of rolling elements is 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 force transmission element, in particular the sleeve, and the shaft. The bearing unit is in particular provided at least to mount the force transmission element and the shaft so that they can rotate against one another and / or at a fixed radial distance relative to one another. The bearing unit preferably comprises at least one bearing element, for example a plain bearing ring or the like. The at least one bearing element is preferably arranged between the force transmission element, in particular the sleeve, and the shaft. The clamping element unit in particular has at least one clamping surface.The force transmission element, in particular the sleeve, preferably has at least one clamping surface. The clamping surface is in particular intended to interact with the at least one rolling body to transmit torque between the force transmission element and the shaft. The clamping element unit preferably has at least one further clamping surface. The further clamping surface is preferably intended to interact with the at least one rolling body to transmit torque between the force transmission element and the shaft. The shaft preferably has a circular cylindrical outer surface. The further clamping surface is preferably formed by the circular cylindrical outer surface of the shaft. Particularly preferably, the at least one rolling body is intended to be clamped to the clamping surface and the further clamping surface to transmit torque between the force transmission element and the shaft.The force transmission element, in particular the sleeve, preferably has an inner surface. The inner surface faces the shaft, in particular. The inner surface preferably has at least one clamping surface. The force transmission element, in particular the sleeve, preferably has at least one recess for arranging the at least one rolling element. The at least one rolling element can be arranged at least partially in the at least one recess. The clamping surface is preferably arranged in the at least one recess of the sleeve, in particular of the force transmission element.Preferably, a number of recesses corresponds to a number of rolling elements of the clamping element unit. Preferably, the at least one recess is designed asymmetrically, in particular at least when viewed in a circumferential direction of the force transmission element, which preferably lies in a plane that runs 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 on the clamping surface and in a free-rotating position. Advantageously, a particularly fast-reacting bidirectional freewheel can be realized. Advantageously, a particularly quiet bidirectional freewheel for a drive unit of an electric bicycle can be realized.

[0014] It is further proposed that the clamping element unit comprise a clamping element holding body. The clamping element holding body preferably has at least one receiving region for the at least one clamping element, in particular the at least one rolling element. The clamping element holding body is preferably annular. In particular, the clamping element holding body is designed as a cage ring. Preferably, a number of receiving regions corresponds to the number of clamping elements, in particular rolling elements, of the clamping element unit. The receiving regions are preferably arranged separately from one another. The at least one receiving region preferably limits a movement of the at least one clamping element, in particular of the at least one rolling element, preferably about the axis of rotation, preferably in the circumferential direction, relative to the clamping element holding body. The clamping element holding body is preferably arranged between the shaft and the force transmission element, in particular the sleeve.The clamping element holding body is preferably arranged so as to be movable relative to the force transmission element, in particular the sleeve, and / or the shaft. In particular, the clamping element holding body is designed to guide the at least one rolling element. It is conceivable for the clamping element, in particular the rolling element, to be arranged on the clamping element holding body without springs. 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 holding 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 mounting on the clamping element holding body by means of spring elements.Alternatively, however, it is also conceivable for the at least one clamping element, in particular the at least one rolling element, to be spring-mounted on the clamping element holding body, preferably in the at least one receiving area. For example, a bearing spring for 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 holding body, preferably in the receiving area. The bearing spring is designed, for example, as a bending spring, as a torsion spring, as a rubber-elastic element or the like. It is conceivable for the bearing spring to be fastened to the clamping element holding body. It is also conceivable for the bearing spring to be formed integrally with the clamping element holding body. A particularly reliable function of the clamping element unit can advantageously be realized.Advantageously, a particularly reliable bidirectional freewheel can be provided.

[0015] It is further proposed that the clamping element unit comprise a mechanical control unit. The control unit is preferably provided for switching between a freewheeling state and a torque transmission state of the freewheel. The freewheeling state is preferably a state of the freewheeling in which torque transmission between the power transmission element and the shaft is interrupted. The torque transmission state is preferably a state of the freewheeling in which torque transmission occurs between the power transmission element and the shaft. A switch between the freewheeling state and the torque transmission state preferably takes place automatically by means of the control unit, in particular free from intervention by a user and / or free from an electronic control system. The control unit is preferably free of electrical components. Alternatively, however, it is also conceivable for the clamping element unit to comprise an electronic control unit.Advantageously, an electrical power supply for controlling the clamping element unit can be dispensed with. It is also proposed that the control unit have a friction unit which is provided for generating an actuating force. The friction unit is provided in particular for moving the clamping element holding body relative to the force transmission element and / or the shaft, preferably for rotating it about the axis of rotation. Particularly preferably, the friction unit is provided at least for releasing a torque transmission state of the freewheel as a function of a relative movement of the force transmission element to the shaft. Preferably, the friction unit is provided at least for switching the freewheel from the torque transmission state of the freewheel to the freewheeling state of the freewheel by means of the actuating force as a function of a relative movement of the force transmission element to the shaft.The friction unit is provided in particular to position the at least one rolling element relative to the force transmission element, in particular the sleeve, and / or the shaft, preferably in order to switch the freewheel, preferably at least from the torque transmission state to the freewheel state. The friction unit is provided to generate a frictional force between the clamping element holding body and a friction body formed separately from the clamping element holding body. Preferably, the friction unit forms a frictional contact between the clamping element holding body and the friction body. The friction unit in particular has at least one friction element. The friction unit preferably comprises a plurality of friction elements, preferably at least two, particularly preferably at least three friction elements. The at least one friction element is provided to form the frictional contact between the clamping element holding body and the friction body.The at least one friction element preferably has at least one friction surface for forming the frictional contact between the clamping element holding body and the friction body. The at least one friction element is preferably fastened to the clamping element holding body. It is conceivable for the at least one friction element to be formed integrally with the clamping element holding body or separately from the clamping element holding body. Alternatively, it is also conceivable for the at least one friction element to be fastened to the friction body, in particular to be formed integrally with the friction body. The friction element is preferably designed as a spring-elastic element, as a rubber-elastic element, or as another friction element that appears appropriate 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 exemplary embodiment, the friction body is connected in a rotationally fixed manner to a housing component of a housing of the drive unit. The friction body is designed, for example, as a friction ring or the like. Alternatively, it is also conceivable for the friction body to be formed by a stationary component of the electric bicycle, in particular of the drive unit. The friction body is alternatively formed, for example, by a frame element of the frame of the electric bicycle, the housing component of the housing of the drive unit or the like. Preferably, the actuating force is a frictional force. In particular, the friction unit is provided to generate the actuating force in at least one operating state of the freewheel by static and / or sliding friction between the clamping element holding body and the friction body.The actuating force, in particular the frictional force, preferably acts, at least in the operating state of the freewheel, counteracting a torque applied to the clamping element holding body. Preferably, the actuating force, preferably the frictional force, is provided to delay rotation of the clamping element holding body about the rotational axis relative to the shaft, in particular at least in the freewheeling state. The clamping element unit is preferably configured to clamp the at least one rolling element in the at least one recess by means of the at least one clamping surface when the rotational speed of the force transmission element in the forward direction of rotation is greater than or equal to the rotational speed of the shaft.When the power transmission element rotates in the forward direction of rotation, wherein a speed of the power transmission element is greater than a speed of the shaft, the friction unit is preferably provided to brake the clamping element holding 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 provided to generate a force on the at least one rolling element via the actuating force, preferably the frictional force, 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, such that the freewheel is preferably switched to the freewheel state.Preferably, the actuating force, in particular the frictional force, can produce a clamping of the at least one rolling body with the power transmission element, in particular 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 rotates forward with respect to the forward direction of rotation. By clamping the at least one rolling body with the power transmission element, in particular the sleeve, and the shaft, a torque can preferably be transmitted between the power transmission element and the shaft. The at least one rolling body is preferably connected in a rotationally fixed manner to the power transmission element, in particular the sleeve, and the shaft in the torque transmission state. The at least one rolling body is in particular in the clamping position when the freewheel is in the torque transmission state.Preferably, the at least one rolling body is arranged so as to rotate freely in the at least one recess in the freewheeling state. Preferably, the at least one rolling body is in a free-rotating position when the freewheel is in the freewheeling state. In particular, the at least one rolling body is arranged so as to rotate freely in the at least one recess when the shaft rotates backwards with respect to the forward direction of rotation. Preferably, the at least one rolling body is arranged so as to rotate freely in the at least one recess when the shaft rotates forwards with respect to the forward direction of rotation and the rotational speed of the shaft is greater than the rotational speed of the force transmission element. Preferably, the at least one rolling body is arranged so as to rotate freely in the at least one recess when the force transmission element rotates backwards with respect to the forward direction of rotation.The clamping element unit is particularly designed to release the at least one rolling element from the clamping position by means of the clamping element holding body 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.

[0016] It is further proposed that the friction unit comprise at least one spring unit. Preferably, the clamping element holding body is connected to the friction body via the spring unit. The spring unit is preferably provided to generate a holding force between the clamping element holding body and the friction body. Preferably, the spring unit is provided to generate the actuating force, in particular the friction 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 spiral spring, as a torsion spring, as a disc spring, as an evolute spring, as an annular 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 holding body.Preferably, the at least one spring element is arranged between the clamping element holding body and the friction body. In particular, the clamping element holding body can be connected to the friction body via the at least one spring element. Advantageously, a mechanical control unit for the clamping element unit can be implemented in a structurally simple manner. Advantageously, a particularly robust mechanical control system for the clamping element unit can be provided. Advantageously, a particularly effective frictional contact can be realized between the clamping element holding body and the friction body.

[0017] Furthermore, it is proposed that the spring unit comprise at least one spiral spring. For example, the at least one spiral spring is formed by the at least one spring element. Preferably, the spring unit is designed free of coil springs. The at least one spiral spring is designed, for example, as a leaf spring, as a wire spring, in particular as a needle spring, as a leg spring, or the like. Advantageously, a particularly effective frictional contact can be realized between the clamping element holding body and the friction body.

[0018] It is further proposed that the spring unit comprise 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 spiral spring. It is conceivable for the leaf spring to be designed as a spiral spring, a bounce spring, an elliptical spring, a parabolic spring, a wave spring or any other leaf spring that would appear appropriate to a person skilled in the art. The leaf spring preferably has at least one spring wing. 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. The friction surface of the friction element is preferably arranged on the at least one spring wing. It is conceivable for the leaf spring to be designed as a single-wing or as an at least double-wing leaf spring. It is conceivable for the friction surface to extend in the axial direction and / or in the radial direction.It is conceivable for the friction surface to be at least partially curved and / or at least partially rectilinear. Preferably, at least one main extension plane of the at least axially extending friction surface runs at least substantially parallel to the axial direction. A “main extension plane” of a structural unit or element can be understood as a plane which is parallel to a largest side surface of the smallest possible imaginary cuboid which just completely encloses the structural unit or element, and which in particular runs through the center of the cuboid. “Substantially parallel” can be understood here as an orientation of a direction relative to a reference direction, in particular in a plane, wherein the direction has a deviation from the reference direction of in particular less than 8°, advantageously less than 5°, and particularly advantageously less than 2°.Preferably, at least the main extension plane of the at least radially extending friction surface runs at least substantially parallel to the radial direction. It is conceivable that the friction surface, in particular extending in the axial direction, is oriented radially inward or radially outward. It is also conceivable that the friction surface, in particular extending in the radial direction, is oriented in the direction of the clamping element holding body or facing away from the clamping element holding body, preferably at least viewed in the axial direction. Advantageously, a particularly effective frictional contact can be realized between the clamping element holding body and the friction body.

[0019] It is also proposed that the leaf spring be designed 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 holding body and the friction body. In particular, the spring with at least two leaves has at least two spring leaves. One of the friction surfaces is preferably arranged on each of the spring leaves. Advantageously, the leaf spring with two leaves can achieve particularly effective frictional contact between the clamping element holding body and the friction body. Advantageously, a particularly large friction surface can be achieved.

[0020] It is further proposed that the spring unit has at least one spring element, in particular the one already mentioned above, which at least largely surrounds an axis of rotation of the freewheel, in particular the one already mentioned above. The fact that an element at least largely surrounds an axis should be understood in particular that the element surrounds the axis by at least 55%, preferably by at least 65%, more preferably by at least 75%, particularly preferably by at least 85% and very particularly preferably by at least 95% in a circumferential direction which lies in a plane which runs perpendicular to the axis. The spring element, which at least largely surrounds the axis of rotation of the freewheel, is preferably annular.It is conceivable that the at least one spring element, which at least largely surrounds the axis of rotation of the freewheel, has at least partially a curved course along its main extent and / or at least partially angled, rectilinear sections along its main extent. Advantageously, a spring unit can be provided which is particularly simple to construct. Advantageously, a particularly large number of contact points can be realized between the at least one spring element and the clamping element holding body. 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 can be realized between the clamping element holding body and the friction body. Advantageously, a spring unit can be realized with a particularly small number of components.Advantageously, a particularly simple and quick assembly of the spring unit on the clamping element holding body can be realized.

[0021] Furthermore, it is proposed that the spring unit has at least one spring element, in particular the one already mentioned above, with at least one mounting ramp. The mounting ramp is provided in particular to guide the at least one spring element during mounting of the spring element on the friction body. Preferably, the mounting ramp is provided to contact the friction body during mounting of the spring element on the friction body and in particular to guide the spring element during a movement in the direction of an intended mounting position. The at least one mounting ramp is preferably arranged on the at least one spring wing of the spring element designed as a leaf spring. The mounting ramp is formed in particular by a surface which runs at an angle to the axis of rotation, preferably different from perpendicular. Advantageously, a particularly simple and / or quick mounting of the clamping element unit on the friction body can be achieved.Advantageously, a particularly fast and cost-effective production of a bidirectional freewheel with a clamping element unit can be achieved.

[0022] Furthermore, it is proposed that the spring unit has at least one spring element, in particular the one already mentioned above, which is designed separately from the clamping element holding body. It is conceivable that the spring element designed separately from the clamping element holding body is fastened to the clamping element holding body or is fastened to the friction body, in particular is designed integrally with the friction body. It is also conceivable that the spring element designed separately from the clamping element holding body is at least partially formed from a material which corresponds to a material of the clamping element holding body or is different from the material of the clamping element holding body. For example, the clamping element holding body is formed from a plastic. Alternatively, however, it is also conceivable that the clamping element holding body is formed from a metal or another material that appears appropriate to a person skilled in the art.Preferably, the at least one spring element is formed from a metal. Alternatively, however, it is also conceivable for the spring element to be formed from a plastic or another material deemed appropriate by a person skilled in the art. Different materials can advantageously be used for the at least one spring element and the clamping element holding body. The materials for the clamping element holding body and the at least one spring element can advantageously be selected particularly suitably. The materials for the clamping element unit can advantageously be selected particularly flexibly, at least with regard to cost, stability, weight, and / or durability.

[0023] It is further proposed that the spring unit comprise at least one spring element, in particular the one already mentioned above, which is fastened to a body separate from the clamping element holding body. The body is preferably a stationary component of the freewheel or of the electric bicycle, in particular of 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 body. It is conceivable that the at least one spring element is formed integrally with the body or is detachably fastened to the body, preferably in a non-destructive manner. Advantageously, the total mass of moving parts of the drive device can be kept low. Advantageously, undesirable inertial forces can be kept low.Advantageously, a particularly responsive clamping element unit can be provided for the bidirectional freewheel.

[0024] It is further proposed that the spring unit comprise at least one spring element, in particular the one already mentioned, which is attached to the clamping element holding body. For example, the spring element is formed integrally with the clamping element holding body, latched, clamped, screwed, or the like to the clamping element holding body. This advantageously allows for particularly reliable positioning of the spring element. This advantageously allows for particularly reliable and precise operation of the clamping element unit, preferably of the control unit.

[0025] Furthermore, it is proposed that the spring unit comprise at least one spring element, in particular the one already mentioned, which is formed integrally with the clamping element holding body. Advantageously, a particularly robust clamping element unit can be provided. Advantageously, a particularly secure connection between the clamping element holding body and the spring elements can be achieved. Advantageously, a control unit for controlling the clamping element unit can be implemented with particularly high reliability.

[0026] Furthermore, it is proposed that the spring unit comprise at least one spring element, in particular the one already mentioned above, which is overmolded by the clamping element holding body. Preferably, the spring element is at least partially overmolded by the clamping element holding body. Advantageously, a particularly secure connection between the clamping element holding body and the spring elements can be achieved. Advantageously, a control unit for controlling the clamping element unit can be realized with particularly high reliability. Advantageously, the at least one spring element is arranged in a particularly captive manner.

[0027] It is further proposed that the friction unit comprise a friction surface extending in the axial direction, in particular the one already mentioned. The axial direction preferably runs parallel to the rotational axis. Advantageously, a particularly compact design of the drive device can be achieved, at least in the radial direction.

[0028] It is further proposed that the friction surface extending in the axial direction be arranged on a side facing the clamping element holding body, viewed in the axial direction. Preferably, in at least one exemplary embodiment, the at least one spring wing of the spring element is arranged on the side facing the clamping element holding body, in particular at least viewed in the axial direction. Advantageously, a particularly compact clamping element unit for the bidirectional freewheel can be realized.

[0029] Furthermore, it is proposed that the friction surface extending in the axial direction be arranged on a side facing away from the clamping element holding body, viewed in the axial direction. Preferably, in at least one exemplary embodiment, the at least one spring wing of the spring element is arranged on the side facing away from the clamping element holding body, in particular at least viewed in the axial direction. Advantageously, a particularly simple assembly of the clamping element holding body to the friction body can be achieved.

[0030] Furthermore, it is proposed that, in particular in at least one exemplary embodiment, the friction surface extending in the axial direction is oriented radially inward when viewed in the radial direction. Preferably, in at least one exemplary embodiment, the at least one friction surface is arranged facing the shaft. In particular, in at least one exemplary embodiment, the at least one friction surface is arranged facing the rotation axis. Advantageously, a particularly compact clamping element unit can be realized with one friction unit. Advantageously, a particularly responsive freewheel with a particularly compact design can be provided.

[0031] It is further proposed that the friction unit 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 of the clamping element holding body, which runs in particular in a plane perpendicular to the axis of rotation. Preferably, the friction elements are arranged uniformly in the circumferential direction on the clamping element holding body or the friction body. Preferably, the friction elements are formed by spring elements of the spring unit. Alternatively, however, it is also conceivable for the friction elements to be arranged unevenly in the circumferential direction, preferably on the clamping element holding body or the friction body. Advantageously, a particularly uniform holding force and / or friction force can be realized between the clamping element holding body and the friction body.Advantageously, a particularly reliable and precise function of the clamping element unit for the bidirectional freewheel can be provided.

[0032] It is also proposed that the drive device comprise at least one force transmission element, in particular the one already mentioned above, for transmitting a drive force of the drive unit, which force transmission element has at least one passage through which the clamping element holding body is guided at least partially outwards in the radial direction. It is conceivable that a number of passages corresponds to a number of friction elements, in particular spring elements. However, it is also conceivable that the number of passages is different from a number of friction elements, in particular spring elements. In particular, in at least one exemplary embodiment, the at least one friction element, preferably the at least one spring element, is at least partially arranged in the at least one passage. In particular, in at least one exemplary embodiment, the at least one passage is free of friction elements, in particular spring elements.Advantageously, a particularly responsive bidirectional freewheel can be designed particularly compactly. Advantageously, weight can be saved by designing the power transmission element with bushings. Furthermore, it is proposed that the drive device comprise at least one power transmission element, in particular the one already mentioned, for transmitting a drive force of 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 spur gears or helical gears. Advantageously, particularly simple assembly of the clamping element unit on the power transmission element can be achieved.

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

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

[0035] Furthermore, it is proposed that a value of a maximum inner diameter of the power transmission element, in particular of the sleeve, be a maximum of 46 mm, in particular the previously mentioned maximum inner diameter. Preferably, a value of the maximum inner diameter of the power transmission element, in particular of the sleeve, is between 40 mm and 41 mm. Alternatively, however, it is also conceivable for a value of the maximum inner diameter of the power transmission element to be greater than 46 mm. Advantageously, a particularly compact drive device with a bidirectional freewheel can be provided.

[0036] Furthermore, it is proposed that a value of a maximum diameter of the rolling element, in particular of the previously mentioned maximum diameter, is a maximum of 5 mm. Preferably, a value of the maximum diameter of the rolling element is substantially 3.5 mm. The fact that a size at least substantially amounts to a specified value should be understood in particular to mean that an actual value of the size deviates from the specified value by a maximum of 10%, particularly preferably a maximum of 5%. Alternatively, however, it is also conceivable that a value of 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 with regard to the rolling elements can be achieved.Advantageously, the high packing density of the rolling elements in the clamping element holding body makes it possible to achieve a particularly reliable and precise bidirectional freewheel. It is further proposed that a maximum angle of movement, in particular translation angle, of the rolling element relative to the clamping element holding body about a rotation axis of the freewheel, in particular the one already mentioned, is a maximum of 1.5°. Preferably, the maximum angle of movement, in particular translation angle, of the at least one rolling element relative to the clamping element holding body is between 0° and 1°. In particular, in an embodiment in which the rolling element is arranged on the clamping element holding body in a spring-mounted manner, the maximum angle of movement, in particular translation angle, of the at least one rolling body relative to the clamping element holding body is particularly preferably substantially 0.5°.Alternatively, however, it is also conceivable that the maximum angle of movement, in particular the translation angle, of the at least one rolling element relative to the clamping element holding body about the rotation axis is greater than 1.5°. This can advantageously provide a particularly responsive and precise bidirectional freewheel.

[0037] It is further proposed that a maximum angle between a clamping position of the rolling body, in particular the previously mentioned clamping position, and a maximum free-rotation position of the rolling body about a rotational axis of the freewheel, in particular the previously mentioned clamping position, is a maximum of 5°. Preferably, the maximum angle between the clamping position of the rolling body and the maximum free-rotation position of the rolling body about the rotational axis of the freewheel is a maximum of 2.5°. Preferably, the maximum angle between the clamping position of the rolling body and the maximum free-rotation position of the rolling body about the rotational axis of the freewheel is between 0.3° and 2.5°, particularly preferably between 0.4° and 2°. Very particularly preferably, the maximum angle between the clamping position of the at least one rolling body and the maximum free-rotation position of the at least one rolling body about the rotational axis is at least substantially 0.8°.The maximum free rotation position and / or the clamping position of the rolling element is / are 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 rear 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 in which the free rotation position of the at least one rolling element is located. In particular, 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 rotation position of the rolling element around the freewheel's rotation axis is greater than 5°. This can advantageously provide a particularly responsive and precise bidirectional freewheel.

[0038] It is also proposed that the clamping element unit and the force transmission element have a common sectional plane which runs at least substantially perpendicular to a rotational axis of the freewheel, in particular the one already mentioned. "Substantially perpendicular" can be understood as an alignment of a direction relative to a reference direction, wherein the direction and the reference direction, in particular 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 particularly advantageously less than 2°. The clamping element unit is preferably arranged at least partially, preferably at least substantially completely, within the force transmission element.The fact that an element is arranged at least substantially completely within a further element should be understood in particular to mean that at least 50%, preferably at least 75%, and particularly preferably at least 90% of a total volume and / or a total mass of the element is arranged within the further element. Particularly preferably, the friction unit, in particular the spring unit, is arranged completely within the force transmission element in at least one exemplary embodiment. Alternatively, it is also conceivable for the clamping element unit to be arranged offset in the axial direction relative to the force transmission element in such a way that at least the external toothing of the force transmission element and the clamping element unit are free of a common sectional plane which runs at least substantially perpendicular to the axis of rotation.Advantageously, a particularly compact drive device with a particularly responsive bidirectional freewheel can be provided. Damage, particularly contamination, to the clamping element unit can be advantageously counteracted.

[0039] Furthermore, it is proposed that the sum of a clamping element holding body angle and a spring angle be smaller than a sleeve clearance angle or equal to the sleeve clearance angle. The clamping element holding body angle is formed in particular by the sum of a clamping element holding body clearance angle and a clamping element holding body loading angle. The clamping element holding body angle is preferably a maximum of 2.5°. Particularly preferably, the clamping element holding body angle is substantially 1.8°. Alternatively, however, it is also conceivable for the clamping element holding body angle to be greater than 2.5°. The clamping element holding body clearance angle corresponds in particular to the maximum angle of movement, in particular translation angle, of the rolling element relative to the clamping element holding body about the rotational axis of the freewheel.The clamping element holding body loading angle is, in particular, a sum of a mechanical clamping element holding body loading angle and a chemical and / or thermal clamping element holding body loading angle. The clamping element holding body loading angle is preferably a maximum of 1°. Particularly preferably, the clamping element holding body loading angle is substantially 0.8°. Alternatively, however, it is also conceivable for the clamping element holding body loading angle to be greater than 1°. The mechanical clamping element holding body loading angle is, in particular, dependent on possible mechanical deformations of the clamping element holding body during operation of the clamping element unit. The mechanical clamping element holding body loading angle is preferably a maximum of 0.7°. Particularly preferably, the mechanical clamping element holding body loading angle is substantially 0.5°.Alternatively, however, it is also conceivable for a value of the mechanical clamping element holding body loading angle to be greater than 0.7°. The chemical and / or thermal clamping element holding body loading angle is particularly dependent 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 loading angle is preferably a maximum of 0.5°. Particularly preferably, the chemical and / or thermal clamping element holding body loading angle is substantially 0.3°. Alternatively, however, it is also conceivable for a value of the chemical and / or thermal clamping element holding body loading angle to be 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 loading angle results in a sleeve angle. The sleeve angle is preferably a maximum of 6.5°, more preferably a maximum of 3.5°. The sleeve angle is particularly preferably substantially 3.3°. Alternatively, however, it is also conceivable for the sleeve angle to be greater than 6.5°. The sleeve loading angle is preferably at least dependent on a 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 loading angle is preferably a maximum of 4°, more preferably a maximum of 2°. The sleeve loading angle is very particularly preferably at least substantially 2.5°. Alternatively, however, it is also conceivable for the sleeve loading angle to have a value greater than 4°. The spring angle is particularly a sum of a spring clearance angle and a spring loading angle.The spring angle is preferably a maximum of 0.1°. More preferably, the spring angle is substantially 0.05°. Alternatively, however, it is also conceivable for the spring angle to be greater than 0.1°. The spring clearance angle relates in particular to any possible play in the connection between the clamping element holding body and the spring unit, in particular the at least one spring element. The spring loading angle is particularly dependent on any possible bending of the at least one spring element. The spring loading angle is preferably a maximum of 0.1°. More preferably, the spring loading angle is substantially 0.05°. Alternatively, however, it is also conceivable for the spring loading angle to be greater than 1°. Advantageously, a particularly reliable function of the clamping element unit for the bidirectional freewheel can be realized.

[0040] 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, preferably at least largely, within the housing of the drive unit. Preferably, the electric motor and / or the transmission are / is arranged, at least largely, within the housing. Advantageously, a particularly robust and / or durable drive unit can be provided. Advantageously, the drive unit can be operated particularly gently.

[0041] 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 comprises the belt means. It is conceivable that at least the housing of the drive unit is at least partially formed integrally with at least part of the frame. Advantageously, an electric bicycle with a particularly responsive bidirectional freewheel can be provided. Advantageously, particularly precise handling, in particular drive behavior, can be realized.

[0042] The drive device according to the invention, the drive unit according to the invention, and / or the electric bicycle according to the invention are not intended to be limited to the application and embodiment described above. In particular, the drive device according to the invention, the drive unit according to the invention, and / or the electric bicycle according to the invention can have a number of individual elements, components, and units that differs from the number stated herein in order to fulfill a function described herein. Furthermore, in the value ranges specified in this disclosure, values ​​within the stated limits are also to be considered disclosed and can be used arbitrarily.

[0043] drawing

[0044] Further advantages will become apparent from the following description of the drawings. The drawings illustrate eight exemplary embodiments of the invention. The drawings, the description, and the claims contain numerous features in combination. Those skilled in the art will also conveniently consider the features individually and combine them into useful further combinations. They show:

[0045] Fig. 1 shows an electric bicycle according to the invention with a drive unit according to the invention in a schematic representation,

[0046] Fig. 2 is a simplified schematic representation of a drive device of the drive unit according to the invention,

[0047] Fig. 3 the drive unit in a perspective sectional view,

[0048] Fig. 4 the drive device in a perspective view,

[0049] Fig. 5 the drive device in an exploded view,

[0050] Fig. 6 a spring element of the drive device,

[0051] Fig. 7 shows a section of a drive device according to the invention of a first alternative embodiment in a schematic representation,

[0052] Fig. 8 shows a section of a drive device according to the invention of a second alternative embodiment in a schematic sectional view,

[0053] Fig. 9 shows a drive device according to the invention of a third alternative embodiment in a schematic representation,

[0054] Fig. 10 shows a drive device according to the invention of a fourth alternative embodiment in a perspective view,

[0055] Fig. 11 shows a section of a drive device according to the invention of a fifth alternative embodiment in a sectional view,

[0056] Fig. 12 shows part of a drive device according to the invention of a sixth alternative embodiment in a perspective view,

[0057] Fig. 13 shows a drive device according to the invention of a seventh alternative embodiment in a perspective view and

[0058] Fig. 14 shows a spring element of the drive device from Figure 13 in a perspective view.

[0059] Description of the Embodiments Figure 1 shows an electric bicycle 14a. The electric bicycle 14a has a frame 68a. The electric bicycle 14a comprises a drive unit 12a. The drive unit 12a is arranged on the frame 68a. The drive unit 12a is arranged in a bottom bracket region 70a of the electric bicycle 14a. The drive unit 12a comprises a housing 72a (see Figure 3). The drive unit 12a comprises an electric motor 74a. The drive unit 12a comprises a transmission 76a for transmitting a drive force of the drive unit 12a, in particular 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 transmission output of the transmission 76a.

[0060] The drive unit 12a comprises at least one drive device 10a. The drive device 10a is arranged at least partially, preferably at least largely, within the housing 72a. Figure 2 shows a simplified diagram of the structure 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 is designed differently 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 for the clamping element unit 18a to be designed as a clamping body unit or as a clamping ball unit. The clamping element unit 18a is arranged on the transmission output of the drive unit 12a.Alternatively, it is also conceivable that the clamping element unit 18a is arranged at a different position within the gear 76a.

[0061] The drive unit 12a comprises at least one pedal crankshaft 105a. The pedal crankshaft 105a can be driven by a user via pedals (not shown). The output pinion 108a is connected to the pedal crankshaft 105a such that the output pinion 108a can be driven by a rotation of the pedal crankshaft 105a, in particular at least in one direction of rotation, preferably in a forward direction of rotation 78a of the drive device 10a. The forward direction of rotation 78a corresponds to a forward movement of the electric bicycle 14a. It is conceivable that a shaft 50a is rotatably mounted and connected to the pedal crankshaft 105a. 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 pedal crankshaft 105a. The further freewheel is preferably provided to prevent the pedal crank shaft 105a from rotating when the shaft 50a is rotating.Alternatively, it is conceivable that the shaft 50a is connected to the pedal crankshaft 105a in a rotationally fixed manner. In particular, it is conceivable that the shaft 50a is formed integrally with the pedal crankshaft 105a. Furthermore, it is conceivable that the shaft 50a corresponds to the pedal crankshaft 105a.

[0062] The drive device 10a comprises at least one power transmission element 42a for transmitting a drive force of 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 for the external teeth to be designed as spur gears or helical gears. Alternatively, however, it is also conceivable for the power transmission element 42a to be designed as a planetary gear, a ring gear, a sun gear, or another power transmission element 42a that would appear appropriate to a person skilled in the art. The power transmission element 42a forms the transmission output of the drive unit 12a. Alternatively, however, it is also conceivable for the power transmission element 42a to be arranged within the transmission 76a and, in particular, to be provided for power transmission to an intermediate shaft of the transmission 76a.

[0063] 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 for the shaft 50a to be designed as an intermediate shaft, which is arranged in particular within the transmission 76a, or the like. The output pinion 108a is connected to the shaft 50a in a rotationally fixed manner. It is conceivable for the output pinion 108a to be formed integrally with the shaft 50a.

[0064] The freewheel 16a has a rotational axis 34a. The shaft 50a and the power transmission element 42a are arranged coaxially around the rotational axis 34a (see also Figures 3, 4, and 5). The shaft 50a, the pedal crankshaft, and / or the power transmission element 42a are / is rotatably mounted about the rotational axis 34a. By rotating the shaft 50a about the rotational axis 34a, a torque can be generated at the output pinion 108a. The clamping element unit 18a is configured 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 a rotational speed of the shaft 50a is greater than a 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 backward relative to the forward direction of the electric bicycle 14a to the shaft 50a, in particular the output pinion 108a, when the rotational speed of the shaft 50a, in particular 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 of the shaft 50a, in particular the output pinion 108a, from the shaft 50a, in particular the output pinion 108a, to the power transmission element 42a, preferably the transmission 76a and / or the electric motor 74a, when the shaft 50a, in particular the output pinion 108a, rotates backward relative to the forward direction of rotation 78a.The clamping element unit 18a is configured 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 gear 76a and / or the electric motor 74a, independently of the rotational speed of the power transmission element 42a and independently of the rotational speed of the shaft 50a, in particular of the output pinion 108a.

[0065] The clamping element unit 18a is provided for decoupling vibrations of a belt 58a. The belt 58a is designed as a chain. Alternatively, it is also conceivable for the belt 58a to be designed as a belt or the like. The belt 58a is preferably connected in a rotationally fixed manner to the output shaft, in particular the output pinion 108a. The belt 58a is provided 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 for the drive wheel 80a to be designed as a front wheel of the electric bicycle 14a.The clamping element unit 18a is provided to counteract the transmission of vibrations of the belt means 58a to components of the drive unit 12a, which are arranged behind the clamping element unit 18a in the drive train, starting from the belt means 58a. The clamping element unit 18a is provided to counteract the transmission of vibrations of the belt means 58a to the transmission 76a and / or the electric motor 74a.

[0066] The clamping element unit 18a comprises a plurality of rolling elements 20a (in the simplified schematic representation in Figure 2, only one rolling element 20a is shown). It is also conceivable for the clamping element unit 18a to comprise only one rolling element 20a. The rolling elements 20a are designed as rollers. Alternatively, it is also conceivable for the rolling elements 20a to be designed as balls, barrels, needles, cones, or other rotating bodies that appear appropriate to a person skilled in the art. In a clamping position of the rolling elements 20a, the rolling elements 20a are provided for torque transmission between the force transmission element 42a and the shaft 50a. In a free-rotating position of the rolling elements 20a, the rolling elements 20a are provided for interrupting torque transmission between the force transmission element 42a and the shaft 50a.

[0067] The clamping element unit 18a comprises at least one sleeve 40a. The sleeve 40a is arranged on the force transmission element 42a. The sleeve 40a is connected to the force transmission element 42a in a rotationally fixed manner. It is conceivable that the sleeve 40a is formed integrally with the force transmission element 42a. It is also conceivable that the sleeve 40a is formed by the force transmission element 42a. The rolling elements 20a are arranged between the force 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 runs in particular in a plane perpendicular to the rotation axis 34a.

[0068] 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 intended to cooperate with at least one of the rolling elements 20a to transmit torque between the force 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 intended to cooperate with at least one of the rolling elements 20a to transmit torque between the force transmission element 42a and the shaft 50a. The shaft 50a has a circular cylindrical surface 86a. The further clamping surface 84a is formed by the circular 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.The number of clamping surfaces 82a corresponds to the number of rolling elements 20a. Each rolling element 20a is assigned one of the clamping surfaces 82a.

[0069] The rolling elements 20a are each provided to be clamped between one of the clamping surfaces 82a and the further clamping surfaces 84a for torque transmission between the force transmission element 42a and the shaft 50a. The sleeve 40a has at least a plurality of recesses 90a for arranging the rolling elements 20a (in the simplified schematic representation in Figure 2, only one recess 90a is shown). 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 designed asymmetrically, in particular at least when viewed in a circumferential direction of the force transmission element 42a, which preferably lies in a plane that runs perpendicular to the rotation axis 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.

[0070] The clamping element unit 18a comprises at least one clamping element holding body 36a (in Figure 2, the clamping element holding body 36a is shown schematically and simplified). The clamping element holding body 36a has a plurality of receiving areas 92a for the rolling elements 20a. The clamping element holding body 36a is annular (see also Figures 4 and 5). The clamping element holding body 36a is designed as a cage ring. A 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 a movement of the rolling elements 20a, in particular about the rotation axis 34a, preferably in the circumferential direction, relative to the clamping element holding body 36a. The clamping element holding body 36a is arranged between the shaft 50a and the force transmission element 42a, in particular the sleeve 40a.The clamping element holding body 36a is arranged to be movable relative to the force transmission element 42a, in particular the sleeve 40a, and / or the shaft 50a. The clamping element holding body 36a is intended to guide the rolling elements 20a.

[0071] The clamping element unit 18a comprises a mechanical control unit 22a. The control unit 22a is designed to switch between a freewheeling state and a torque-transmitting state of the freewheel 16a. The freewheeling 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-transmitting 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 freewheeling state and the torque-transmitting state occurs automatically by means of the control unit 22a, in particular without user intervention and / or without electronic control. The control unit 22a is free of electrical components. Alternatively, however, it is also conceivable for the clamping element unit 18a to comprise an electronic control unit.

[0072] The control unit 22a has a friction unit 24a, which is provided for generating an actuating force. The friction unit 24a is provided for moving the clamping element holding body 36a relative to the force transmission element 42a and / or the shaft 50a, in particular for rotating it about the rotation axis 34a. The friction unit 24a is provided at least for releasing a torque transmission state of the freewheel 16a, depending on a relative movement of the force transmission element 42a to the shaft 50a. The friction unit 24a is provided at least for switching the freewheel 16a from the torque transmission state of the freewheel 16a to the freewheel state of the freewheel 16a, depending on a relative movement of the force transmission element 42a to the shaft 50a, by means of the actuating force.The friction unit 24a is provided to position the rolling elements 20a relative to the force transmission element 42a, in particular the sleeve 40a, and / or the shaft 50a, preferably in order to switch the freewheel 16a, preferably at least from the torque transmission state to the freewheel state.

[0073] The friction unit 24a is provided for generating a frictional force between the clamping element holding body 36a and a friction body 94a formed separately from the clamping element holding body 36a. The friction body 94a is a stationary component of the freewheel 16a. The friction body 94a is designed as a friction ring. The friction body 94a is connected in a rotationally fixed manner to a housing component 62a of the housing 72a. Alternatively, it is also conceivable for the friction body 94a to be formed by a stationary component of the electric bicycle 14a, in particular the drive unit 12a. The friction body 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 holding body 36a and the friction body 94a.The friction unit 24a has a plurality of friction elements 66a (in the simplified schematic representation in Figure 2, only two friction elements 66a are shown). The friction unit 24a has four friction elements 66a. Alternatively, it is also conceivable for the friction unit 24a to have a number of friction elements 66a that is different from 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 in particular runs in a plane perpendicular to the rotation axis 34a.

[0074] The friction elements 66a each have two friction surfaces 38a for forming the frictional contact between the clamping element holding body 36a and the friction body 94a. Alternatively, it is also conceivable for the friction elements 66a to each have only one friction surface 38a or more than two friction surfaces 38a. Alternatively, however, it is also conceivable for the friction elements 66a to be arranged unevenly in the circumferential direction, preferably on the clamping element holding body 36a or the friction body 94a. The friction elements 66a are fastened to the clamping element holding body 36a. The friction elements 66a are formed integrally with the clamping element holding body 36a. The actuating force is a frictional force. The friction unit 24a is provided 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 holding body 36a and the friction body 94a.The actuating force, in particular the frictional force, acts, at least in the operating state of the freewheel 16a, counteracting a torque applied to the clamping element holding body 36a. The actuating force, preferably the frictional force, is intended to delay rotation of the clamping element holding body 36a about the rotational axis 34a relative to the shaft 50a, in particular at least in the freewheeling state.

[0075] The drive device 10a comprises at least one bearing unit 96a, which is arranged at least partially between the force transmission element 42a, in particular the sleeve 40a, and the shaft 50a. The bearing unit 96a is provided at least to support the force transmission element 42a and the shaft 50a so that they can rotate relative to one another and / or at a fixed radial distance relative to one another. The bearing unit 96a comprises at least two bearing elements 54a. Alternatively, it is also conceivable for the bearing unit 96a to comprise only one bearing element 54a or more than two bearing elements 54a. The bearing elements 54a are designed as plain bearing rings. The bearing elements 54a are arranged between the force transmission element 42a, in particular the sleeve 40a, and the shaft 50a.

[0076] The clamping element unit 18a is configured to clamp the rolling elements 20a in the recesses 90a by means of the respective clamping surface 82a when the rotational speed of the force transmission element 42a in the forward rotational direction 78a is greater than or equal to the rotational speed of the shaft 50a. When the force transmission element 42a rotates in the forward rotational direction 78a, wherein a rotational speed of the force transmission element 42a is greater than a rotational speed of the shaft 50a, the friction unit 24a is provided to brake the clamping element holding body 36a relative to the force 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 to clamp them.The clamping element unit 18a is provided to generate a force on the rolling elements 20a via the actuating force, in particular the frictional force, when the shaft 50a rotates backward 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 freewheel state. The actuating force, in particular the frictional force, can be used to clamp the rolling elements 20a to the force transmission element 42a, in particular the sleeve 40a, and the shaft 50a when the rotational speed of the force transmission element 42a is greater than the rotational speed of the shaft 50a, preferably at least when the force transmission element 42a rotates forward relative to the forward direction of rotation 78a.By clamping the rolling elements 20a with the force transmission element 42a, in particular the sleeve 40a, and the shaft 50a, a torque can be transmitted between the force transmission element 42a and the shaft 50a.

[0077] In the torque-transmitting state, the rolling elements 20a are non-rotatably connected to the force-transmitting element 42a, in particular the sleeve 40a, and the shaft 50a. The rolling elements 20a are located, in particular, in the clamping position when the freewheel 16a is in the torque-transmitting state. In the freewheeling state, the rolling elements 20a are arranged to rotate freely in the recesses 90a. In particular, the rolling elements 20a are arranged to rotate freely in the recesses 90a when the freewheel 16a is in the freewheeling state. The rolling elements 20a are arranged to rotate freely in the recesses 90a when the shaft 50a rotates backward relative to the forward direction of rotation 78a. The rolling elements 20a are each arranged freely rotating 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 in the recesses 90a so as to rotate freely when the power transmission element 42a rotates backward relative to the forward rotation direction 78a. The clamping element unit 18a is provided to release the rolling elements 20a from the clamping by means of the clamping element holding body 36a when the rotational speed of the shaft 50a is greater than the rotational speed of the power transmission element 42a.

[0078] The friction unit 24a comprises at least one spring unit 26a. The clamping element holding body 36a is connected to the friction body 94a via the spring unit 26a. The spring unit 26a is provided to generate a holding force between the clamping element holding body 36a and the friction body 94a. The spring unit 26a is provided to generate the actuating force, in particular the friction force, of the friction unit 24a. The spring unit 26a has four spring elements 32a. Alternatively, however, it is also conceivable for the spring unit 26a to have a number of spring elements 32a that is different from 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 for the spring elements 32a to be designed as torsion springs, disc springs, evolute springs, ring springs, or the like. Furthermore, it is also conceivable for the spring elements 32a to be 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 holding 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 Figure 6). The mounting ramps 60a are formed by surfaces that are angled to the rotation axis 34a and preferably extend in a direction other than perpendicular.

[0079] The spiral springs 28a are designed as leaf springs 30a. Alternatively, it is also conceivable for the spiral springs 28a to be designed as wire springs, needle springs, leg springs, or the like. Preferably, the spring unit 26a is designed free of coil springs. The leaf springs 30a are designed as at least two-winged leaf springs. Alternatively, however, it is also conceivable for the leaf springs 30a to be designed as single-winged leaf springs, as spiral springs, as rebound springs, as elliptical springs, as parabolic springs, as wave springs, or as other leaf springs 30a that would be deemed appropriate by a person skilled in the art. The leaf springs 30a each have two spring wings 56a (see Figure 6). The friction surfaces 38a of the friction elements 66a are each arranged on the spring wings 56a.

[0080] The rolling elements 20a are arranged spring-free on the clamping element holding body 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 holding body 36a, preferably at least in the respective receiving area 92a, is free of spring elements. The rolling elements 20a are free of any mounting on the clamping element holding body 36a by means of spring elements.

[0081] The spring elements 32a are fastened to the clamping element holding body 36a. The spring elements 32a are formed from a material that is different from a material from which the clamping element holding body 36a is formed. The spring elements 32a are formed from metal. Alternatively, however, it is also conceivable for the spring elements 32a to be formed from a plastic or another material that appears appropriate to a person skilled in the art. The clamping element holding body 36a is formed from a plastic. Alternatively, however, it is also conceivable for the clamping element holding body 36a to be formed from a metal or another material that appears appropriate to a person skilled in the art. Alternatively, however, it is also conceivable for the spring elements 32a and the clamping element holding body 36a to be formed from an identical material. The spring elements 32a are formed in one piece with the clamping element holding body 36a. The spring elements 32a are overmolded by the clamping element holding body 36a.The spring elements 32a are at least partially overmolded by the clamping element holding body 36a.

[0082] The spring elements 32a each have two connecting elements 106a for connecting the spring elements 32a to the clamping element holding body 36a. The connecting elements 106a are designed as openings. Alternatively, however, it is also conceivable for the connecting elements 106a to be designed as other connecting elements 106a that would appear appropriate to a person skilled in the art. The connecting elements 106a are intended to be injection-molded through by the clamping element holding body 36a during production 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 holding body 36a in an assembly position prior to overmolding. The mounting elements 104a are designed as openings.Alternatively, however, it is also conceivable for the mounting elements 104a to be designed as projections or as other mounting elements 104a that would be deemed appropriate by a person skilled in the art. The friction surfaces 38a of the friction unit 24a, in particular of the friction elements 66a, extend in the axial direction. The axial direction runs parallel to the rotation axis 34a. The friction surfaces 38a are at least partially curved. Alternatively or additionally, it is conceivable for the friction surfaces 38a to extend at least partially in a straight line. The friction surfaces 38a each have a main plane of extension that runs at least substantially parallel to the axial direction.

[0083] The friction surfaces 38a extending in the axial direction are arranged on a side facing away from the clamping element holding body 36a, 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, in particular at least viewed in the axial direction. The friction surfaces 38a extending in the axial direction are oriented inwardly, viewed in the radial direction. The friction surfaces 38a are arranged facing the shaft 50a. The friction surfaces 38a are arranged facing the rotation axis 34a.

[0084] The force transmission element 42a has four passages 44a through which the clamping element holding body 36a is guided at least partially outward in the radial direction. Alternatively, it is also conceivable for the force transmission element 42a to have a number of passages 44a that differs from four, for example, only one passage 44a, two, three, or more than four passages 44a. A number of passages 44a corresponds in particular to a number of friction elements 66a, in particular spring elements 32a. However, it is alternatively also conceivable for the number of passages 44a to differ from a number of friction elements 66a, in particular spring elements 32a.

[0085] A value of a maximum diameter 46a of the rolling elements 20a is between 6% and 20% of a value of a maximum inner diameter 48a of the force transmission element 42a, in particular of the sleeve 40a. Preferably, a value of the maximum diameter 46a of the rolling elements 20a is a maximum of 15%, particularly preferably a maximum of 10% of a value of the maximum inner diameter 48a of the force transmission element 42a, in particular of the sleeve 40a. Alternatively, however, it is also conceivable for a value of the maximum diameter 46a of the rolling elements 20a to be outside a range between 6% and 20% of a value of the maximum inner diameter 48a of the force transmission element 42a, in particular of the sleeve 40a. The inner diameter 48a is measured in particular in the radial direction. Preferably, the maximum diameter 46a is measured in the radial direction.A value of the maximum diameter 46a of the rolling elements 20a is between 8% and 25% of a value of a maximum diameter 52a of the shaft 50a. Preferably, a value of the maximum diameter 46a of the rolling elements 20a is a maximum of 15%, particularly preferably a maximum of 12% of a value of the maximum diameter 52a of the shaft 50a. Alternatively, however, it is also conceivable that a value of the maximum diameter 46a of the rolling elements 20a is outside a range between 8% and 25% of a value 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.

[0086] A value of the maximum diameter 52a of the shaft 50a is, for example, a maximum of 38 mm, particularly preferably a value of the maximum diameter 52a of the shaft 50a is 32 mm. A value of the maximum inner diameter 48a of the force transmission element 42a, in particular of the sleeve 40a, is a maximum of 45 mm. Preferably, a value of the maximum inner diameter 48a of the force transmission element 42a, in particular of the sleeve 40a, is between 40 mm and 41 mm. Alternatively, however, it is also conceivable that a value of the maximum inner diameter 48a of the force transmission element 42a, in particular of the sleeve 40a, is greater than 45 mm. A value of the maximum diameter 46a of the rolling elements 20a is a maximum of 5 mm. Preferably, a value of the maximum diameter 46a of the rolling elements 20a is substantially 3.5 mm. Alternatively, however, it is also conceivable that a value of the maximum diameter 46a of the rolling elements 20a is greater than 5 mm.

[0087] A respective maximum angle of movement, in particular a translation angle, of the rolling elements 20a relative to the clamping element holding body 36a about the rotation axis 34a of the freewheel 16a is a maximum of 1.5°. Preferably, the maximum angle of movement, in particular translation angle, of the rolling elements 20a relative to the clamping element holding body 36a is between 0° and 1°. Particularly preferably, the respective maximum angle of movement, in particular translation angle, of the rolling elements 20a relative to the clamping element holding body 36a is substantially 0.5°. Alternatively, however, it is also conceivable that the respective maximum angle of movement, in particular translation angle, of the rolling elements 20a relative to the clamping element holding body 36a about the rotation axis 34a is greater than 1.5°.

[0088] 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 rotation axis 34a of the freewheel 16a is 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 rotation axis 34a of the freewheel 16a is 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 rotation axis 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 rotation axis 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, in which 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 rotation axis 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 rest against the respective stop of the recesses 90a. The clamping element unit 18a and the force transmission element 42a have a common sectional plane which runs 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 for the clamping element unit 18a to be arranged offset in the axial direction from the force transmission element 42a in such a way that at least the external toothing of the force transmission element 42a and the clamping element unit 18a are free of a common sectional plane which runs at least substantially perpendicular to the axis of rotation 34a.

[0089] The sum of a cage angle and a spring angle is smaller than or equal to a sleeve clearance angle. The clamping element holding body angle is formed by the sum of a clamping element holding body clearance angle and a clamping element holding body loading angle. The clamping element holding body angle is a maximum of 2.5°. The clamping element holding body angle is particularly preferably substantially 1.8°. Alternatively, however, it is also conceivable for the clamping element holding body angle to be greater than 2.5°. The clamping element holding 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 holding body 36a about the rotational axis 34a of the freewheel 16a. The clamping element holding body loading angle is the sum of a mechanical clamping element holding body loading angle and a chemical and / or thermal clamping element holding body loading angle.The clamping element holding body loading angle is a maximum of 1°. Particularly preferably, the clamping element holding body loading angle is substantially 0.8°. Alternatively, however, it is also conceivable for the clamping element holding body loading angle to be greater than 1°. The mechanical clamping element holding body loading angle depends in particular on possible mechanical deformations with respect to the clamping element holding body 36a during operation of the clamping element unit 18a. The mechanical clamping element holding body loading angle is a maximum of 0.7°. Particularly preferably, the mechanical clamping element holding body loading angle is substantially 0.5°. Alternatively, however, it is also conceivable for a value of the mechanical clamping element holding body loading angle to be greater than 0.7°.The chemical and / or thermal clamping element holding body loading angle is particularly dependent 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 loading angle is a maximum of 0.5°. Particularly preferably, the chemical and / or thermal clamping element holding body loading angle is substantially 0.3°. Alternatively, however, it is also conceivable for a value of the chemical and / or thermal clamping element holding body loading angle to be greater than 0.5°.

[0090] 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 loading angle results in a sleeve angle. The sleeve angle is a maximum of 6.5°, preferably a maximum of 3.5°. Particularly preferably, the sleeve angle is substantially 3.3°. Alternatively, however, it is also conceivable for the sleeve angle to be greater than 6.5°. The sleeve loading angle is preferably at least dependent 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 loading angle is a maximum of 4°, preferably a maximum of 2°. Very particularly preferably, the sleeve loading angle is at least substantially 2.5°.Alternatively, however, it is also conceivable for the sleeve loading angle to have a value greater than 4°. The spring angle is in particular a sum of a spring clearance angle and a spring loading 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 for the spring angle to be greater than 0.1°. The spring clearance angle relates in particular to a possible play in the connection between the clamping element holding body 36a and the spring unit 26a, in particular the spring elements 32a. The spring loading angle is particularly dependent on a possible bending of the respective spring elements 32a. The spring loading angle is preferably a maximum of 0.1°. Particularly preferably, the spring loading angle is substantially 0.05°. Alternatively, however, it is also conceivable for the spring loading angle to be 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.

[0091] Further exemplary embodiments of the invention are shown in Figures 7 to 14. The following descriptions and the drawings are essentially limited to the differences between the exemplary embodiments, whereby with regard to components with the same designation, in particular with regard to components with the same reference symbols, reference can in principle also be made to the drawings and / or the description of the other exemplary embodiments, in particular Figures 1 to 6. To distinguish the exemplary embodiments, the letter a is placed after the reference symbols of the exemplary embodiment in Figures 1 to 6. In the exemplary embodiments in Figures 7 to 14, the letter a is replaced by the letters b to h.

[0092] 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 body 94b. The drive device 10b comprises at least one force transmission element 42b for transmitting a drive force of the drive unit.

[0093] The spring unit 26b has four spring elements 32b, which are formed separately from a clamping element holding body 36b of the clamping element unit 18b (only one of the four spring elements 32b is shown in Figure 7). The spring elements 32b are arranged between the friction body 94b and the clamping element holding body 36b. The spring elements 32b are clamped between the friction body 94b and the clamping element holding body 36b. The spring elements 32b can be flexibly arranged along a circumferential direction of the friction body 94b and / or the clamping element holding body 36b between the clamping element holding body 36b and the friction body 94b and can be clamped in particular for fixing. Alternatively, it is also conceivable for the spring elements 32b to be fastened to the clamping element holding body 36b or to be fastened to the friction body 94b, in particular to be formed integrally with the friction body 94b. The spring elements 32b are designed as bending springs 28b, in particular as leaf springs 30b.The friction unit 24b has friction surfaces 38b. The friction surfaces 38b are arranged on the spring elements 32b. The friction surfaces 38b are oriented radially inward. The spring elements 32b are formed, in particular, from a material that is different from a material from which the clamping element holding body 36b is formed. Alternatively, however, it is also conceivable that the material from which the spring elements 32b are formed corresponds to the material from which the clamping element holding body 36b is formed. The clamping element unit 18b comprises at least one sleeve 40b. The clamping element unit 18b comprises a plurality of rolling elements 20b.

[0094] Figure 8 shows a drive device 10c for a drive unit (not shown here) of an electric bicycle (not shown here). The drive device 10c has a bidirectional freewheel 16c. The freewheel 16c has at least one clamping element unit 18c. The clamping element unit 18c comprises at least one mechanical control unit 22c. The control unit 22c has at least one friction unit 24c, which is provided for generating an actuating force. The friction unit 24c has at least one spring unit 26c. The freewheel 16c has at least one friction body 94c. The drive device 10c comprises at least one force transmission element 42c for transmitting a drive force of the drive unit. The spring unit 26c has four spring elements 32c. The spring elements 32c are formed separately from a clamping element holding body 36c of the clamping element unit 18c.The spring elements 32c are designed as spiral springs 28c, in particular as leaf springs 30c. The friction body 94c is surrounded radially outward by the clamping element holding body 36c. Friction surfaces 38c of the friction unit 24c face radially inward.

[0095] Figure 9 shows a drive device 10d for a drive unit (not shown here) of an electric bicycle (not shown here). The drive device 10d has a bidirectional freewheel 16d. The freewheel 16d has at least one clamping element unit 18d. The clamping element unit 18d comprises at least one clamping element holding body 36d. The freewheel 16d has at least one friction body 94d. The drive device 10d comprises at least one force transmission element 42d for transmitting a drive force of the drive unit. The force transmission element 42d has four passages 44d through which the clamping element holding body 36d is guided at least partially outward in the radial direction.

[0096] The clamping element unit 18d comprises at least one mechanical control unit 22d. The control unit 22d has at least one friction unit 24d, which is provided for generating an actuating force. The friction unit 24d has at least one spring unit 26d. The spring unit 26d comprises a spring element 32d. The spring element 32d surrounds at least a large part of a rotational axis 34d of the freewheel 16d. The spring element 32d is annular. The spring element 32d has rectilinear sections 98d along its main extent, which are angled relative to one another (in Figure 9, only three of the sections 98d are provided with reference numerals by way of example). Alternatively or additionally, it is also conceivable for the spring element 32d to be at least partially curved along its main extent. The spring element 32d, the clamping element holding body 36d, the force transmission element 42d and the friction body 94d are arranged coaxially to the rotation axis 34d.

[0097] Figure 10 shows a drive device 10e for a drive unit (not shown here) of an electric bicycle (not shown here). The drive device 10e has a bidirectional freewheel 16e. The freewheel 16e has at least one clamping element unit 18e. The clamping element unit 18e comprises at least one clamping element holding body 36e. The freewheel 16e has at least one friction body 94e. The drive device 10e comprises at least one force transmission element 42e for transmitting a drive force of the drive unit. The force transmission element 42e has four passages 44e through which the clamping element holding body 36e is guided at least partially outward in the radial direction. The clamping element unit 18e comprises at least one sleeve 40e.

[0098] The clamping element unit 18e comprises at least one mechanical control unit 22e. The control unit 22e has at least one friction unit 24e, which is provided for generating an actuating force. The friction unit 24e has at least one spring unit 26e. The spring unit 26e comprises a spring element 32e. The spring element 32e surrounds at least a large part of a rotation axis 34e of the freewheel 16e. The spring element 32e is annular. The spring element 32e has a curved, in particular continuous, profile along its main extent. Friction surfaces 38e of the friction unit 24e are formed by the clamping element holding body 36e. The clamping element holding body 36e has four finger elements 100e. Alternatively, it is also conceivable that the clamping element holding body 36e has a number of finger elements 100e that is different from four, for example one, two, three or more than four finger elements 100e.The finger elements 100e extend radially outward through the passages 44e. The finger elements 100e each have a clamping projection 102e at a respective free end of the finger elements 100e. The spring element 32e rests against the clamping projections 102e. The spring element 32e exerts a holding force on the friction body 94e via the clamping projections 102e. The spring element 32e generates the actuating force, in particular a friction force, via the clamping element holding body 36e, in particular between the clamping element holding body 36e and the friction body 94e.

[0099] Figure 11 shows a drive device 10f for a drive unit (not shown here) of an electric bicycle (not shown here). The drive device 10f has a bidirectional freewheel 16f. The freewheel 16f has at least one clamping element unit 18f. The drive device 10f comprises at least one force transmission element 42f for transmitting a drive force of the drive unit. The clamping element unit 18f comprises at least one sleeve 40f. The clamping element unit 18f comprises a plurality of rolling elements 20f (only one of the rolling elements 20f is shown in Figure 11).

[0100] The clamping element unit 18f comprises at least one mechanical control unit 22f. The control unit 22f has at least one friction unit 24f, which is provided for generating an actuating force. The friction unit 24f has at least one spring unit 26f. The clamping element unit 18f comprises a clamping element holding body 36f. The spring unit 26f comprises four spring elements 32f (only one of the four spring elements 32f is shown in Figure 11). The spring elements 32f are designed as spiral springs 28f, in particular as leaf springs 30f. The spring elements 32f are fastened to a body separate from the clamping element holding body 36f. The body is a housing component 62f of a housing 72f of the drive unit. The freewheel 16f has at least one friction body 94f. The friction body 94f is formed by the housing component 62f. The spring elements 32f are detachably attached to the body, in particular in a non-destructive manner.Alternatively, it is also conceivable for the spring elements 32f to be formed integrally with the body, preferably at least partially overmolded by the body. The spring elements 32f are each secured to the body, in particular the housing component 62f, by at least one fastening element 64f. The fastening elements 64f are designed as screws, bolts, locking elements, clamping elements, or the like.

[0101] The friction unit 24f comprises at least one friction surface 38f extending in the axial direction. A friction surface 38f extending in the axial direction is arranged on each of the spring elements 32f. The friction surfaces 38f extending in the axial direction are arranged on a side facing the clamping element holding body 36f. The spring elements 32f each have a spring wing 56f. The respective spring wing 56f of the spring elements 32f is arranged on the side facing the clamping element holding body 36f, in particular at least viewed in the axial direction.

[0102] Figure 12 shows a drive device 10g for a drive unit (not shown here) of an electric bicycle (not shown here). The drive device 10g has a bidirectional freewheel 16g. The freewheel 16g has at least one clamping element unit 18g. The clamping element unit 18g comprises at least one clamping element holding body 36g. The clamping element unit 18g comprises a plurality of rolling elements 20g.

[0103] The clamping element unit 18g comprises at least one mechanical control unit 22g. The control unit 22g has at least one friction unit 24g, which is provided for generating an actuating force. The friction unit 24g has at least one spring unit 26g. The spring unit 26g comprises four spring elements 32g. The spring elements 32g are designed as spiral springs 28g, in particular as leaf springs 30g. The spring elements 32g are clamped to the clamping element holding body 36g. In particular, the four spring elements 32g each have a clamping projection 102g. The clamping projections 102g are designed such that a deflection of the clamping projections 102g can be generated by arranging the spring elements 32g on the clamping element holding body 36g in an operating position. The deflection of the clamping projections 102g generates a restoring force which acts on the clamping element holding body 36g and thus in particular clamps the spring elements 32f to the clamping element holding body 36g.Friction surfaces 38g of the friction unit 24g face radially outward. The friction surfaces 38g are arranged on the spring elements 32g.

[0104] Figure 13 shows a drive device 10h for a drive unit (not shown here) of an electric bicycle (not shown here). The drive device 10h comprises at least one power transmission element 42h for transmitting a drive force of the drive unit. The drive device 10h comprises at least one bearing unit 96h. The bearing unit 96h is provided at least to mount the power transmission element 42h and a shaft (not shown here) of the drive device 10h so that they can rotate relative to one another and / or at a fixed radial distance from one another. The bearing unit 96h comprises at least two bearing elements 54h. The drive device 10h has a bidirectional freewheel 16h.

[0105] The clamping element unit 18h comprises at least one clamping element holding body 36h. The clamping element unit 18h comprises a plurality of rolling elements 20h. The force transmission element 42h has four passages 44h through which the clamping element holding body 36h is guided at least partially outward in the radial direction. The freewheel 16h has at least one clamping element unit 18h. The clamping element unit 18h comprises at least one mechanical control unit 22h. The control unit 22h has at least one friction unit 24h, which is provided for generating an actuating force. The friction unit 24h has at least one spring unit 26h.

[0106] The spring unit 26h has four spring elements 32h. The four spring elements 32h each have two mounting ramps 60h (see Figure 14). Alternatively, it is also conceivable for the spring elements 32h each to have only one mounting ramp 60h or more than two mounting ramps 60h. The mounting ramps 60h are provided to guide the spring elements 32h during assembly of the spring elements 32h on a friction body (not shown here). The mounting ramps 60h are provided to contact the friction body during assembly of the spring elements 32h on the friction body and in particular to guide the spring elements 32h during a movement towards a designated assembly position. The mounting ramps 60h are arranged on spring wings 56h of the spring elements 32h. The spring elements 32h are designed as spiral springs 28h, in particular as leaf springs 30h. Friction surfaces 38h of the friction unit 24h are arranged on the spring elements 32h.The friction surfaces 38h extend in the axial direction. The friction surfaces 38h extending in the axial direction are oriented outward when viewed in the radial direction.

Claims

Claims 1. Drive device (10a - 10h) for a drive unit (12a - 12h) of an electric bicycle (14a - 14h), with a bidirectional freewheel (16a - 16h), characterized in that the freewheel (16a - 16h) comprises at least one clamping element unit (18a - 18h).

2. Drive device (10a - 10h) according to claim 1 , characterized in that the clamping element unit (18a - 18h) is provided for decoupling vibrations of a wrapping means (58a - 58h).

3. Drive device (10a - 10h) according to claim 1 or 2, characterized in that the clamping element unit (18a - 18h) comprises at least one rolling element (20a - 20h), in particular a roller.

4. Drive device (10a - 10h) according to one of the preceding claims, characterized in that the clamping element unit (18a - 18h) comprises a clamping element holding body (36a - 36h).

5. Drive device (10a - 10h) according to one of the preceding claims, characterized in that the clamping element unit (18a - 18h) comprises a mechanical control unit (22a - 22h).

6. Drive device (10a - 10h) according to claim 5, characterized in that the control unit (22a - 22h) has a friction unit (24a - 24h) which is provided for generating an actuating force.

7. Drive device (10a - 10h) according to claim 6, characterized in that the friction unit (24a - 24h) has at least one spring unit (26a - 26h).

8. Drive device (10a - 10h) according to claim 7, characterized in that the spring unit (26a - 26h) comprises at least one bending spring (28a - 28h) 9. Drive device (10a - 10h) according to claim 7, characterized in that the spring unit (26a - 26h) comprises at least one leaf spring (30a - 30h).

10. Drive device (10a; 10h) according to claim 9, characterized in that the leaf spring (30a; 30h) is designed as a leaf spring with at least two leaves.

11. Drive device (10d; 10e) according to claim 7, characterized in that the spring unit (26d: 26e) has at least one spring element (32d; 32e) which surrounds at least a large part of a rotation axis (34d; 34e) of the freewheel (16d; 16e).

12. Drive device (10a; 10h) according to claim 7, characterized in that the spring unit (26a; 26h) has at least one spring element (32a; 32h) with at least one mounting ramp (60a; 60h).

13. Drive device (1 Ob - 10g) at least according to claim 4 and claim 7, characterized in that the spring unit (26b - 26g) has at least one spring element (32b - 32g) which is designed separately from the clamping element holding body (36b - 36g).

14. Drive device (1 Of) according to claims 4 and 7, characterized in that the spring unit (26f) has at least one spring element (32f) which is attached to a body separate from the clamping element holding body (36f).

15. Drive device (10a - 10e; 10g; 10h) according to claims 4 and 7, characterized in that the spring unit (26a - 26e; 26g; 26h) has at least one spring element (32a - 32e; 32g; 32h) which is attached to the clamping element holding body (36a - 36e; 36g; 36h).

16. Drive device (1 Oa; 10h) at least according to claims 4 and 7, characterized in that the spring unit (26a; 26h) has at least one spring element (32a; 32h) which is formed integrally with the clamping element holding body (36a; 36h).

17. Drive device (10a; 10h) at least according to claims 4 and 7, characterized in that the spring unit (26a; 26h) has at least one spring element (32a; 32h) which is overmolded by the clamping element holding body (36a; 36h).

18. Drive device (10a - 10h) according to claim 6, characterized in that the friction unit (24a - 24h) comprises a friction surface (38a - 38h) extending in an axial direction 19. Drive device (1 Of - 10h) according to claims 4 and 18, characterized in that the friction surface (38f - 38h) extending in the axial direction is arranged, viewed in the axial direction, on a side facing the clamping element holding body (36f - 36h).

20. Drive device (10a) according to claims 4 and 18, characterized in that the friction surface (38a) extending in the axial direction is arranged on a side facing away from the clamping element holding body (36a) when viewed in the axial direction.

21. Drive device (10a - 10f) according to claim 18, characterized in that the friction surface (38a - 38f) extending in the axial direction is oriented inwards when viewed in the radial direction.

22. Drive device (1 Oa - 10c; 10f - 10h) according to claims 4 and 6, characterized in that the friction unit (24a - 24c; 24f - 24h) comprises at least two friction elements (66a - 66c; 66f - 66h) for generating an actuating force, wherein the friction elements (66a - 66c; 66f - 66h) are arranged uniformly in the circumferential direction of the clamping element holding body (36a - 36c; 36f - 36h).

23. Drive device (10a - 10h) according to claim 4, characterized by a force transmission element (42a - 42h) for transmitting a drive force of the drive unit (12a - 12h), which has at least one passage (44a - 44h) through which the clamping element retaining body (36a - 36h) is guided at least partially in a radial direction outwards.

24. Drive device (10a - 10h) according to one of the preceding claims, characterized by a power transmission element (42a - 42h) for transmitting a drive force of the drive unit (12a - 12h), which is designed as a spur gear.

25. Drive device (10a - 10h) according to claim 3, characterized by a force transmission element (42a - 42h) for transmitting a drive force of the drive unit (12a - 12h), wherein a value of a maximum diameter (46a - 46h) of the at least one rolling element (20a - 20h) is between 6% and 20% of a value of a maximum inner diameter (48a - 48h) of the force transmission element (42a - 42h). Drive device (10a - 10h) according to claim 3, characterized by a shaft (50a - 50h), wherein the maximum diameter (46a - 46h) of the at least one rolling element (20a - 20h) is between 8% and 25% of the maximum diameter (52a - 52h) of the shaft (50a - 50h). Drive device (10a - 10h) according to any one of the preceding claims, characterized by a power transmission element (42a - 42h) for transmitting a drive force from the drive unit (12a - 12h), wherein the maximum inner diameter (48a - 48h) of the power transmission element (42a - 42h) is a maximum of 46 mm. Drive device (10a - 10h) according to claim 3, characterized in that a value of a maximum diameter (46a - 46h) of the rolling element (20a - 20h) is a maximum of 5 mm.Drive device (10a - 10h) according to claims 3 and 4, characterized in that a maximum angle of movement, in particular translation angle, of the rolling element (20a - 20h) relative to the clamping element retaining body (36a - 36h) about an axis of rotation (34a - 34h) of the freewheel (16a - 16h) is a maximum of 1.5°. Drive device (10a - 10h) according to claim 3, characterized in that a maximum angle between a clamping position of the rolling element (20a - 20h) and a maximum free rotation position of the rolling element (20a - 20h) about an axis of rotation (34a - 34h) of the freewheel (16a - 16h) is a maximum of 5°.Drive device (10a - 10h) according to one of the preceding claims, characterized by a force transmission element (42a - 42h) for transmitting a drive force of the drive unit (12a - 12h), wherein the clamping element unit (18a - 18h) and the force transmission element (42a - 42h) have a common cutting plane which is at least substantially perpendicular to an axis of rotation (34a - 34h) of the freewheel (16a - 16h).

32. Drive device (1 Oa - 10h) according to one of the preceding claims, characterized in that a sum of a cage angle and a spring angle is less than or equal to a sleeve clearance angle.

33. Drive unit (12a - 12h) for an electric bicycle (14a - 14h) with a drive device (10a - 10h) according to one of the preceding claims.

34. Electric bicycle (14a - 14h) with a drive unit (12a - 12h) according to claim 33.

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