Driving device of driving unit of electric bicycle, driving unit and electric bicycle

Abstract

The invention relates to a method for operating an electric bicycle (14a; 12b) of the drive unit (14a; 10b) for driving a drive device (10a; 10b) having a two-way freewheel (16a; 16b), the free wheel (16a; 16b) comprises at least one clamping element unit (18a; 18b) for a motor vehicle. According to the invention, the clamping element unit (18a; 18b) comprises at least one pretensioning unit (112a; 112b), which is provided for generating a preload force. The invention also relates to a method for operating an electric bicycle (14a; 12b) of the drive unit (14a; 12b) and a corresponding electric bicycle (14a; 14b) for a motor vehicle.

Description

Technical Field

[0001] The invention relates to a driving device for a driving unit of an electric bicycle, a driving unit for an electric bicycle and an electric bicycle. Background Art

[0002] A drive device for a drive unit of an electric bicycle has been proposed, which has a bidirectional freewheel comprising at least one clamping element unit. Summary of the invention

[0003] The invention relates to a drive device for a drive unit of an electric bicycle, having a bidirectional freewheel, which comprises at least one clamping element unit.

[0004] It is proposed that the clamping element unit includes at least one preload unit configured to generate a preload force. Preferably, the freewheel is configured as a freewheel based on force locking. The clamping element unit is preferably configured as a clamping body unit, a clamping ball unit or a clamping roller unit. The freewheel is particularly configured to be different from the pawl freewheel. Preferably, the drive unit includes an electric motor. The drive unit particularly includes a transmission device for transmitting the driving force of the drive unit to the driven pinion of the drive unit. The driven pinion is, for example, configured as a sprocket or the like. The driven pinion is preferably connected to the transmission output end of the transmission device. Preferably, the clamping element unit is arranged on the transmission output end of the drive unit. Alternatively, it is conceivable that the clamping element unit is arranged at other positions in the transmission device. Alternatively, the drive device can also be used in a transport device different from an electric bicycle. It is conceivable that the transport device includes an internal combustion engine, an electric motor or a similar device.

[0005] The drive device preferably comprises at least one force transmission element for transmitting the driving force of the drive unit. Preferably, the clamping element unit is arranged on the force transmission element. The force transmission element can be configured as a spur gear, a planetary gear, a hollow gear, a sun gear or other force transmission elements that professionals consider useful. Preferably, the force transmission element forms the transmission output of the drive unit. However, it is conceivable that the force transmission element is arranged inside the transmission and is particularly configured to transmit force to the intermediate shaft of the transmission. Preferably, the drive device comprises at least one shaft. Preferably, the shaft is configured as a driven shaft. However, it is also conceivable that the shaft is configured as an intermediate shaft particularly arranged inside the transmission or as a similar shaft. Preferably, the driven pinion is connected to the shaft configured as a driven shaft in a rotationally fixed manner. It is conceivable that the driven pinion is constructed integrally with the driven shaft. "Integral" can be understood as being connected at least materially, for example by a welding process, an adhesive process, an injection molding process and / or other processes that a professional considers useful, and / or as being advantageously formed into a piece, for example by manufacturing with a casting device or by a single-component or multi-component injection molding method and advantageously from a single-piece blank.

[0006] The drive unit preferably comprises at least one pedal crankshaft. Preferably, the pedal crankshaft can be driven by the user via the pedal. The drive device has a forward rotation direction, which corresponds in particular to the forward movement of the electric bicycle. Preferably, the driven pinion is connected to the pedal crankshaft in such a way that the driven pinion can be driven by the rotation of the pedal crankshaft, in particular at least in one rotation direction, preferably in the forward rotation direction of the drive device. It is conceivable that the shaft is connected to the pedal crankshaft in a rotatably supported manner. In addition, it is conceivable that the drive unit has another freewheel arranged between the shaft and the pedal crankshaft. The other freewheel is preferably arranged to prevent the pedal crankshaft from rotating with the shaft when the shaft rotates. Alternatively, it is conceivable that the shaft is connected to the pedal crankshaft in a rotationally fixed manner. In particular, it is conceivable that the shaft is constructed integrally with the pedal crankshaft. In addition, it is conceivable that the shaft is equivalent to the pedal crankshaft. Preferably, the shaft and the force transmission element are arranged coaxially with the rotation axis of the freewheel. In particular, the shaft, the pedal crank shaft and / or the force transmission element are mounted so as to be rotatable about the rotation axis.

[0007] Preferably, the clamping element unit is designed to interrupt the transmission of a motor torque directed forwards relative to the forward direction of the electric bicycle to the shaft, in particular to the driven pinion, when the rotational speed of the shaft is greater than the rotational speed of the force transmission element driven by the motor torque. It is also conceivable that the clamping element unit is designed to interrupt the transmission of a motor torque directed backwards relative to the forward direction of the electric bicycle to the shaft, in particular to the driven pinion, when the rotational speed of the shaft, in particular to the driven pinion, is greater than the rotational speed of the force transmission element driven by the motor torque. Preferably, the clamping element unit is designed to interrupt the transmission of the torque of the shaft, in particular to the driven pinion, from the shaft, in particular to the driven pinion, to the force transmission element (preferably a transmission and / or an electric motor) when the shaft, in particular to the driven pinion rotates backwards relative to the forward direction, in particular to the forward rotational direction of the electric bicycle. Preferably, the clamping element unit is configured to interrupt the transmission of the torque of the shaft, in particular the driven pinion, from the shaft, in particular the driven pinion, to the force transmission element, preferably to the transmission and / or the electric motor, independently of the rotational speed of the force transmission element and independently of the rotational speed of the shaft, in particular the driven pinion.

[0008] Preferably, the clamping element unit comprises at least one clamping element. Preferably, the clamping element is arranged to transmit a torque between the force transmission element and the shaft in a clamped state of the clamping element, in particular between the force transmission element and the shaft. Preferably, the at least one clamping element is arranged to interrupt the torque transmission between the force transmission element and the shaft when the clamping element is in a state decoupled from the force transmission element and / or the shaft, in particular when the clamping element is in a state of free rotation and / or spaced apart from the force transmission element and / or the shaft. The clamping element is, for example, configured as a rolling body, as a non-circular clamping body or the like. Preferably, the clamping element is configured differently from a pawl. It is also conceivable that the clamping element unit comprises a plurality of clamping elements, in particular at least two, preferably at least three clamping elements.

[0009] By means of this configuration of the drive device, a particularly fast-acting bidirectional freewheel can be advantageously provided for the drive unit of the electric bicycle. Advantageously, a particularly low-noise bidirectional freewheel can be realized for the drive unit of the electric bicycle. Advantageously, a particularly gentle operation of the drive unit, in particular the transmission and / or the electric motor can be realized by means of the drive device. Advantageously, an undesired transmission of torque from the shaft to the force transmission element through the movement of the shaft in any rotational direction can be counteracted. Advantageously, an undesired transmission of torque from the output side to at least one part of the electric motor and / or the transmission can be counteracted.

[0010] Preferably, the clamping element unit is configured to decouple the vibration of the winding device. The winding device is configured, for example, as a chain, a drive belt or the like. Preferably, the winding device is connected to the driven shaft, in particular the driven pinion, in a rotationally fixed manner. The winding device is particularly configured to transmit the driving force from the shaft, which is preferably configured as the driven shaft, in particular from the driven pinion, to the drive wheel of the electric bicycle. Preferably, the drive wheel is configured as the rear wheel of the electric bicycle. However, it is also conceivable that the drive wheel is configured as the front wheel of the electric bicycle. The clamping element unit is preferably configured to resist the transmission of the vibration of the winding device to the component of the drive unit arranged behind the clamping element unit in the drive train starting from the winding device. The clamping element unit is preferably configured to resist the transmission of the vibration of the winding device to the transmission device and / or the electric motor. Advantageously, particularly gentle operation can be ensured. Advantageously, a particularly durable drive device, preferably a drive unit, in particular a particularly durable electric motor and / or a particularly durable transmission device can be provided by using the clamping element unit. Advantageously, transmission noise can be resisted. Advantageously, the vibrations of the winding component can be decoupled in a particularly low-noise manner.

[0011] Preferably, the clamping element unit comprises at least one rolling body, in particular a roller. Alternatively, it is also conceivable that the rolling body is configured as a ball, a barrel, a needle, a cone or other rotating body that is considered useful by the person skilled in the art. Preferably, the rolling body is configured to be rotationally symmetrical. At least one rolling body is preferably arranged to transmit torque between the force transmission element and the shaft when the rolling body is in a clamped state. At least one rolling body is preferably arranged to interrupt the torque transmission between the force transmission element and the shaft when the rolling body is in a freely rotating state. Preferably, the clamping element unit 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 particularly arranged on the force transmission element. Preferably, the sleeve is connected to the force transmission element in a rotationally fixed manner. Preferably, the sleeve is constructed integrally with the force transmission element. It is also conceivable that the sleeve is formed by the force transmission element. The at least one sleeve is particularly arranged between the force transmission element, in particular the sleeve, and the shaft. The rolling bodies are preferably arranged uniformly. Preferably, a plurality of rolling bodies are arranged uniformly along the circumference of the shaft, which preferably extends in a plane perpendicular to the axis of rotation. Preferably, the drive device comprises at least one bearing unit, which is at least partially arranged between the force transmission element, in particular a sleeve, and the shaft. The bearing unit is in particular at least configured to support the force transmission element and the shaft so that they can rotate relative to each other and / or are spaced at a fixed radial distance relative to each other. Preferably, the bearing unit comprises at least one bearing element, such as a plain bearing ring or the like. Preferably, at least one bearing element is arranged between the force transmission element, in particular a sleeve, and the shaft. The clamping element unit has in particular at least one clamping surface. The force transmission element, in particular a sleeve, preferably has at least one clamping surface. The clamping surface is in particular configured to cooperate with at least one rolling body in order to transmit a torque between the transmission element and the shaft. Preferably, the clamping element unit has at least one further clamping surface. Preferably, the further clamping surface is configured to cooperate with the at least one rolling body in order to transmit a torque between the transmission element and the shaft. Preferably, the shaft has a cylindrical outer circumference. Preferably, the further clamping surface is formed by the cylindrical outer circumference of the shaft. Particularly preferably, at least one rolling body is arranged to be clamped by the clamping surface and the further clamping surface for transmitting a torque between the force transmission element and the shaft. Preferably, the force transmission element, in particular a sleeve, has an inner surface. The inner surface is particularly oriented toward the shaft. Preferably, the inner surface has at least one clamping surface. Preferably, the force transmission element, in particular a sleeve, has at least one recess for arranging at least one rolling body. The at least one rolling body is at least partially arranged in the at least one recess. Preferably, the clamping surface is arranged in at least one recess of the sleeve, in particular the force transmission element. Preferably, the number of recesses corresponds to the number of rolling bodies of the clamping element unit. Preferably, in particular, at least one recess is constructed asymmetrically, at least when viewed in the circumferential direction of the force transmission element, preferably in a plane extending perpendicularly to the axis of rotation.Preferably, at least one recess is designed such that at least one rolling body can be arranged in the recess in a clamped position on a clamped surface and in a freely rotating position. Advantageously, a particularly responsive bidirectional freewheel can be realized. Advantageously, a particularly low-noise bidirectional freewheel can be realized for an electric bicycle drive unit.

[0012] Preferably, the clamping element unit comprises a clamping element holder. Preferably, the clamping element holder has at least one receiving area for at least one clamping element, in particular at least one rolling body. The clamping element holder is preferably designed in an annular manner. The clamping element holder is in particular designed as a cage ring. Preferably, the number of receiving areas corresponds to the number of clamping elements, in particular rolling bodies, of the clamping element unit. The receiving areas are preferably arranged spaced apart from one another. Preferably, at least one receiving area delimits the movement of at least one clamping element, in particular at least one rolling body, preferably about an axis of rotation, preferably in the circumferential direction relative to the clamping element holder. Preferably, the clamping element holder is arranged between the shaft and the force transmission element, in particular a sleeve. Preferably, the clamping element holder is arranged to be movable relative to the force transmission element, in particular a sleeve, and / or the shaft. The clamping element holder is in particular provided for guiding at least one rolling body. It is also conceivable that the clamping element, in particular a rolling body, is arranged on the clamping element holder without a spring. Preferably, the at least one receiving area for at least one clamping element, in particular at least one rolling body, has no spring element. In particular, the region between at least one clamping element, preferably at least one rolling body, and the clamping element holder is free of spring elements, in particular at least in the receiving region. Preferably, at least one clamping element, in particular at least one rolling body, is not supported on the clamping element holder by means of a spring element. Alternatively, however, it is also conceivable that at least one clamping element, in particular at least one rolling body, is arranged on the clamping element holder in a spring-supported manner, preferably in at least one receiving region. For example, a supporting spring for elastically supporting at least one clamping element is arranged between at least one clamping element, in particular at least one rolling body, and the clamping element holder, preferably in the receiving region. The supporting spring is designed, for example, as a bending spring, a torsion spring, a rubber elastic element or the like. It is conceivable that the supporting spring is fixed to the clamping element holder. It is also conceivable that the supporting spring is constructed integrally with the clamping element holder. Advantageously, a particularly reliable function of the clamping element unit can be achieved. Advantageously, a particularly reliable bidirectional freewheel can be provided.

[0013] Preferably, the clamping element unit comprises a mechanical control unit. Preferably, the control unit is configured to switch between an idling state and a torque transmission state of the freewheel. The idling state is preferably such a state of the freewheel in which the torque transmission between the force transmission element and the shaft is interrupted. The torque transmission state is preferably such a state of the freewheel in which the torque transmission between the force transmission element and the shaft is carried out. Preferably, the switch between the idling state and the torque transmission state is carried out automatically by means of the control unit, in particular without user intervention and / or without electronic control. The control unit preferably has no electrical components. However, it is also conceivable as an alternative that the clamping element unit comprises an electrical control unit. Advantageously, an electrical energy supply for controlling the clamping element unit can be omitted.

[0014] Preferably, the control unit comprises a friction unit, which is configured to generate an adjustment force. The friction unit is particularly configured to move the clamping element holder relative to the force transmission element and / or the shaft, preferably to rotate it about the axis of rotation. Particularly preferably, the friction unit is at least configured to release the torque transmission state of the freewheel according to the relative movement of the force transmission element and the shaft. Preferably, the friction unit is at least configured to switch the freewheel from the torque transmission state of the freewheel to the freewheel idling state by the adjustment force according to the relative movement of the force transmission element and the shaft. The friction unit is particularly configured to position at least one rolling body 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 idling state. The friction unit is configured to generate a friction force between the clamping element holder and a friction body configured separately from the clamping element holder. Preferably, a friction contact is formed between the clamping element holder and the friction body by the friction unit. The friction unit particularly has at least one friction element. Preferably, the friction unit comprises a plurality of friction elements, preferably at least two, particularly preferably at least three friction elements. At least one friction element is arranged to form a friction contact between the clamping element holder and the friction body. At least one friction element preferably has at least one friction surface for forming a friction contact between the clamping element holder and the friction body. At least one friction element is preferably fixed on the clamping element holder. It is conceivable that at least one friction element is integrally constructed with the clamping element holder or is separately constructed from the clamping element holder. Alternatively, it is also conceivable that at least one friction element is fixed on the friction body, in particular integrally constructed with the friction body. The friction element is preferably constructed as a spring elastic element, a rubber elastic element or other friction elements that professionals consider useful. The friction body is preferably formed by a fixed component of the free wheel. In particular, in at least one embodiment, the friction body and the housing component of the housing of the drive unit are connected in a torsion-proof manner. The friction body is, for example, constructed as a friction ring or a similar structure. Alternatively, it is also conceivable that the friction body is formed by a fixed component of the electric bicycle, in particular the drive unit. The friction body is alternatively formed, for example, by a frame element of the frame of the electric bicycle, a housing component of the housing of the drive unit or the like. Preferably, the adjustment force is a friction force. The friction unit is particularly designed to generate an adjustment force between the clamping element holder and the friction body by static friction and / or sliding friction in at least one operating state of the freewheel. The adjustment force, in particular the friction force, preferably counteracts a torque acting on the clamping element holder at least in this operating state of the freewheel. The adjustment force, preferably the friction force, is preferably designed to delay a rotation of the clamping element holder about the axis of rotation relative to the shaft, in particular at least in the idling state. The clamping element unit is preferably designed to clamp at least the rolling body in at least one gap by means of at least one clamping surface when the rotational speed of the force transmission element in the forward rotational direction is greater than or equal to the rotational speed of the shaft.When the force transmission element rotates in the forward rotational direction, wherein the rotational speed of the force transmission element is greater than the rotational speed of the shaft, the friction unit is preferably configured to brake the clamping element holding body relative to the force transmission element by means of an adjustment force, in particular a friction force, so that preferably at least one rolling body is brought into contact with and clamped in at least one recess of the force transmission element, in particular a sleeve. The clamping element unit is particularly configured to generate a force on the at least one rolling body by means of an adjustment force, in particular a friction force, when the shaft rotates in a rearward direction relative to the forward rotational direction, in order to preferably disengage the at least one rolling body from the at least one clamping surface, so that the freewheel is preferably switched into an idle state. Preferably, at least when the force transmission element rotates in a forward direction relative to the forward rotational direction, when the rotational speed of the force transmission element is greater than the rotational speed of the shaft, preferably by means of an adjustment force, in particular a friction force, a clamping of the at least one rolling body with the force transmission element, in particular a sleeve, and the shaft can be generated. By clamping the at least one rolling body with the force transmission element, in particular a sleeve, and the shaft, a torque can preferably be transmitted between the force transmission element and the shaft. At least one rolling body is preferably connected to the force transmission element, in particular the sleeve, and the shaft in a torque transmission state in a rotationally fixed manner. When the freewheel is in the torque transmission state, the at least one rolling body is in particular in a clamped position. Preferably, the at least one rolling body is freely rotatably arranged in the at least one gap in the idling state. Preferably, when the freewheel is in the idling state, the at least one rolling body is in a freely rotatable position. In particular, when the shaft rotates backward relative to the forward rotational direction, the at least one rolling body is freely rotatably arranged in the at least one gap. Preferably, when the shaft rotates forward relative to the forward rotational direction and the rotational speed of the shaft is greater than the rotational speed of the force transmission element, the at least one rolling body is freely rotatably arranged in the at least one gap. Preferably, when the force transmission element rotates backward relative to the forward rotational direction, the at least one rolling body is freely rotatably arranged in the at least one gap. The clamping element unit is particularly configured to release the clamping of the at least one rolling body by means of the clamping element retaining body when the rotational speed of the shaft is greater than the rotational speed of the force transmission element. Advantageously, the mechanical control unit for the clamping element unit can be realized in a structurally simple manner. Advantageously, a particularly robust mechanical control of the clamping element unit can be provided.

[0015] Preferably, the friction unit has at least one spring unit. Preferably, the clamping element holding body is connected to the friction body via the spring unit. Preferably, the spring unit is arranged to generate a holding force between the clamping element holding body and the friction body. Preferably, the spring unit is arranged to generate an adjustment force, in particular a friction force, of the friction unit. The spring unit, for example, has at least one spring element. Preferably, at least one friction element is formed by at least one spring element. It is conceivable that at least one spring element is configured as a bending spring, a torsion spring, a disc spring, a spiral spring or the like. Alternatively, it is conceivable that the spring element is configured as a rubber elastic element. Preferably, at least one spring element is arranged on the clamping element holding body. Preferably, 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 at least one spring element. Advantageously, a mechanical control unit for the clamping element unit can be realized in a structurally simple manner. Advantageously, a particularly strong mechanical control can be provided for the clamping element unit. Advantageously, a particularly effective friction contact between the clamping element holding body and the friction body can be realized.

[0016] Preferably, the spring unit comprises at least one bending spring. For example, the at least one bending spring is formed by the at least one spring element. Preferably, the spring unit is designed without a helical spring. The at least one bending spring is designed, for example, as a leaf spring, a wire spring, in particular a needle spring, a helical torsion spring or the like. Advantageously, a particularly effective frictional contact between the clamping element holder and the friction body can be achieved.

[0017] Preferably, the spring unit comprises at least one leaf spring. Preferably, at least one leaf spring is formed by the at least one spring element, in particular the at least one bending spring. It is conceivable that the leaf spring is configured as a helical spring, a buffer spring, an elliptical spring, a parabolic spring, a wave spring or other leaf springs that the skilled person considers useful. The leaf spring preferably has at least one spring wing. In particular, at least one friction surface of the friction unit is arranged on at least one spring element, in particular a leaf spring. Preferably, the friction surface of the friction element is arranged on at least one spring wing. It is conceivable that the leaf spring is configured as a single-wing or at least double-wing leaf spring. It is conceivable that the friction surface extends in the axial direction and / or in the radial direction. It is conceivable that the friction surface is at least partially curved and / or extends at least partially straight. Preferably, at least one main extension plane of the friction surface extending in the axial direction extends at least substantially parallel to the axial direction. The "main extension plane" of a structural unit or element can be understood as a plane that is parallel to the largest side of the smallest possible imaginary cuboid that just completely surrounds the structural unit or element, and the plane extends in particular through the center of the cuboid. "Substantially parallel" can be understood as an orientation of a direction relative to a reference direction, in particular in a plane, wherein the direction has a deviation of less than 8°, advantageously less than 5°, particularly advantageously less than 2° relative to the reference direction. Preferably, at least the main extension plane of the friction surface extending radially extends at least substantially parallel to the radial direction. It is conceivable that the friction surface extending in particular in the axial direction is oriented radially inwards or radially outwards. It is also conceivable that the friction surface extending in particular in the radial direction is preferably oriented toward the clamping element holder or away from the clamping element holder, at least when viewed in the axial direction. Advantageously, a particularly effective friction contact between the clamping element holder and the friction body can be achieved.

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

[0019] The spring unit has, for example, at least one spring element, in particular, as already mentioned above, which at least largely surrounds the freewheel axis, in particular, as already mentioned above. An element at least largely surrounding an axis should be understood in particular to mean that the element surrounds the axis in a circumferential direction of the axis in a plane extending perpendicularly to the axis by at least 55%, preferably at least 65%, preferably at least 75%, particularly preferably at least 85% and completely particularly preferably at least 95%. The spring element that at least largely surrounds the freewheel axis is preferably designed in an annular shape. It is conceivable that at least one spring element that at least largely surrounds the freewheel axis has a curved course at least partially along its main extension and / or has straight sections that extend at an angle to each other along its main extension at least partially. Advantageously, a spring unit that can be realized particularly simply in terms of structure can be provided. Advantageously, particularly many contact points between at least one spring element and the clamping element retaining body can be realized. Advantageously, particularly many contact locations between the at least one spring element and the friction body can be realized. Advantageously, a particularly effective and / or uniform frictional contact between the clamping element holder and the friction body can be achieved. Advantageously, a spring unit with a particularly small number of components can be achieved. Advantageously, a particularly simple and rapid assembly of the spring unit on the clamping element holder can be achieved.

[0020] The spring unit comprises, for example, at least one spring element, in particular, as mentioned previously, having at least one mounting ramp. The mounting ramp is in particular provided for guiding the spring element when it is mounted on the friction body. The mounting ramp is preferably provided for contacting the friction body when the spring element is mounted on the friction body and in particular for guiding the spring element when it moves in the direction of the set mounting position. At least one mounting ramp is preferably arranged on at least one spring wing of a spring element configured as a leaf spring. The mounting ramp is in particular formed by a plane that is angularly bent relative to the axis of rotation, preferably extending differently from the vertical. Advantageously, a particularly simple and / or rapid mounting of the clamping element unit on the friction body can be achieved. Advantageously, a particularly rapid and low-cost manufacturing of a bidirectional freewheel with a clamping element unit can be achieved.

[0021] The spring unit comprises, for example, at least one spring element, in particular, as mentioned previously, which is constructed separately from the clamping element retaining body. It is conceivable that the spring element constructed separately from the clamping element retaining body is fixed to the clamping element retaining body or to the friction body, in particular, is constructed integrally with the friction body. It is also conceivable that the spring element constructed separately from the clamping element retaining body is at least partially formed by a material that matches or is different from the material of the clamping element retaining body. For example, the clamping element retaining body is formed of plastic. However, it is also conceivable that the clamping element retaining body is formed of metal or other materials that the technician considers useful. Preferably, the clamping element retaining body is formed of metal. However, it is also conceivable that the spring element is formed of plastic or other materials that the technician considers useful. Advantageously, different materials can be used for at least one spring element and the clamping element retaining body. Advantageously, materials can be selected particularly appropriately for the clamping element retaining body and the at least one spring element. Advantageously, materials can be selected particularly flexibly for the clamping element unit at least with respect to cost, stability, weight and / or durability.

[0022] The spring unit has, for example, at least one spring element, in particular one already mentioned, which is fixed to a body separate from the clamping element retaining body. Preferably, the body is a stationary component of the freewheel or of the electric bicycle, in particular of the drive unit. For example, the body is formed by a housing component of the drive unit, by a frame element or the like. It is conceivable that the body is formed by a friction body. It is conceivable that at least one spring element is integrally formed with the body or is preferably fixed to the body in a manner that allows it to be disassembled without damage. Advantageously, the total mass of the movable part of the drive device can be kept small. Advantageously, unexpected inertial forces can be kept small. Advantageously, a fast-reacting clamping element unit can be provided for a bidirectional freewheel.

[0023] The spring unit comprises, for example, at least one spring element, in particular one already mentioned above, which is fixed to the clamping element holder. For example, the spring element is integrally formed with the clamping element holder, is latched, clamped, screwed or the like to the clamping element holder. Advantageously, a particularly secure position of the spring element can be achieved. Advantageously, a particularly secure and precise function of the clamping element unit, preferably of the control unit, can be achieved.

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

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

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

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

[0028] Alternatively, the friction surface extending in the axial direction is arranged, for example, on a side facing away from the clamping element holder when viewed in the axial direction. Preferably, in at least one embodiment, at least one spring wing of the spring element is arranged on a side facing away from the clamping element holder when viewed in the axial direction at least. Advantageously, a particularly simple assembly of the clamping element holder on the friction body can be achieved.

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

[0030] The friction unit preferably comprises at least two friction elements, in particular those already mentioned above, for generating an adjustment force, wherein the friction elements are arranged uniformly in the circumferential direction of the clamping element retaining body, the circumference extending 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 retaining body or on the friction body. Preferably, the friction elements are formed by spring elements of a spring unit. Alternatively, however, it is also conceivable that the friction elements are preferably arranged uniformly in the circumferential direction on the clamping element retaining body or on the friction body. Advantageously, a particularly uniform holding force and / or friction force between the clamping element retaining body and the friction body can be achieved. Advantageously, a particularly reliable and precise functioning of the clamping element unit of a bidirectional freewheel can be provided.

[0031] The drive device preferably comprises at least one force transmission element, in particular the previously mentioned one, for transmitting the driving force of the drive unit, which has at least one through-hole, through which the clamping element retaining body is at least partially led outward in the radial direction. It is conceivable that the number of through-holes corresponds to the number of friction elements, in particular spring elements. However, it is also conceivable that the number of through-holes is different from the number of friction elements, in particular spring elements. In particular, in at least one embodiment, at least one friction element, preferably at least one spring element, is at least partially arranged in at least one through-hole. In particular, in at least one embodiment, at least one through-hole is free of friction elements, in particular spring elements. Advantageously, a particularly fast-reacting bidirectional freewheel can be realized in a particularly compact manner. Advantageously, weight can be saved by the configuration of the force transmission element with a through-hole.

[0032] The drive device preferably comprises at least one force transmission element, in particular the one already mentioned above, for transmitting the driving force of the drive unit, wherein the force transmission element is designed as a spur gear. The spur gear preferably has an external toothing. It is conceivable that the external toothing is designed as a straight toothing or as a helical toothing. Advantageously, a particularly simple assembly of the clamping element unit on the force transmission element can be achieved.

[0033] Preferably, the value of the maximum diameter of at least one rolling body is 6% to 20% of the value of the maximum inner diameter of the force transmission element, in particular a sleeve. Preferably, the value of the maximum diameter of at least one rolling body is at most 15%, particularly preferably at most 10%, of the value of the maximum inner diameter of the force transmission element, in particular a sleeve. Alternatively, however, it is also conceivable that the value of the maximum diameter of at least one rolling body lies outside the range of 6% to 20% of the value of the maximum inner diameter of the force transmission element, in particular a 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 rolling bodies can be achieved. Advantageously, a particularly reliable and precise bidirectional freewheel can be achieved by the high packing density of rolling bodies in the clamping element retaining body.

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

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

[0036] The value of the maximum diameter of the rolling body, in particular the value already mentioned above, is preferably a maximum of 5 mm. Preferably, the value of the maximum diameter of the rolling body is substantially 3.5 mm. "The value specified is at least substantially" is to be understood in particular as meaning that the actual value of this value deviates from the specified value by a maximum of 10%, particularly preferably by a maximum of 5%. Alternatively, however, it is also conceivable that the value of the maximum diameter of the rolling body is greater than 5 mm. Advantageously, a particularly compact drive device with a bidirectional freewheel can be provided. Advantageously, a clamping element unit with a particularly high packing density of the rolling bodies can be achieved. Advantageously, a particularly reliable and precise bidirectional freewheel can be achieved by the high packing density of the rolling bodies in the clamping element retaining body.

[0037] The maximum movement angle, in particular the translation angle, of the rolling body relative to the clamping element holder about the previously mentioned freewheel rotation axis is preferably at most 1.5°. Preferably, the maximum movement angle, in particular the translation angle, of at least one rolling body relative to the clamping element holder is between 0° and 1°. In one embodiment in particular, the rolling body is elastically supported on the clamping element holder. Particularly preferably, the maximum movement angle, in particular the translation angle, of at least one rolling body relative to the clamping element holder is substantially 0.5°. Alternatively, however, it is also conceivable that the maximum movement angle, in particular the translation angle, of at least one rolling body relative to the clamping element holder is greater than 1.5°. Advantageously, a particularly responsive and precise bidirectional freewheel can be provided.

[0038] The maximum angle between the clamping position of the rolling body, in particular the one already mentioned above, and the maximum free rotation position of the rolling body about the freewheeling axis, in particular the one already mentioned above, is preferably 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 freewheeling axis is 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 freewheeling axis 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 at least one rolling body and the maximum free rotation position of at least one rolling body about the axis of rotation is substantially 0.8°. The maximum free rotation position and / or the clamping position of the rolling body are in particular in at least one recess for at least one rolling body. The maximum free rotation position and the clamping position are preferably in mutually opposite end regions of the recess. Preferably, at least one further clamping surface is arranged on the rear side of the recess with respect to the forward rotational direction. Preferably, the free rotation position is arranged on the front side of the recess with respect to the forward rotational direction. In particular, the recess has a stop for the at least one rolling body in the end region, in particular in which the free rotation position of the at least one rolling body is located. In particular, the rolling body is in a maximum free rotation position when it abuts against the stop of the recess. Alternatively, it is also conceivable that the maximum angle between the clamped position of the rolling body and the maximum free rotation position about the freewheel axis is greater than 5°. Advantageously, a particularly responsive and precise bidirectional freewheel can be provided.

[0039] The clamping element unit and the force transmission unit preferably have a common cross section, which extends at least substantially perpendicularly to the freewheel axis of rotation, in particular already mentioned above. "Substantially perpendicularly" can be understood as an orientation of a direction relative to a reference direction, wherein, in particular when viewed in a projection plane, the direction and the reference direction enclose an angle of 90° and the angle has a maximum deviation of in particular less than 8°, preferably less than 5° and particularly preferably less than 2°. The clamping element unit is preferably arranged at least partially, preferably at least substantially completely, inside the force transmission element. An element being arranged at least substantially completely inside another element should be understood in particular to mean that at least 50%, preferably at least 75% and particularly preferably at least 90% of the total volume and / or total mass of the element is arranged inside the other element. Particularly preferably, the friction unit, in particular the spring unit, is arranged completely inside the force transmission element in at least one embodiment. Alternatively, it is also conceivable that the clamping element unit is arranged offset in the axial direction relative to the force transmission element so that at least the outer toothing of the force transmission element and the clamping element unit do not have a common cross section extending at least substantially perpendicularly to the axis of rotation. Advantageously, a particularly compact drive device with a particularly fast-reacting bidirectional freewheel can be provided. Advantageously, damage to the clamping element unit, in particular contamination, can be prevented.

[0040] The sum of the clamping unit holding body angle and the spring angle is preferably less than or equal to the sleeve free angle. The clamping element holding body angle is formed in particular by the sum of the clamping unit holding body free angle and the clamping unit holding body load angle. The clamping unit holding body angle is preferably a maximum of 2.5°. It is particularly preferred that the clamping element holding body angle is substantially 1.8°. However, it is conceivable that the clamping unit holding body angle is greater than 2.5°. The clamping unit holding body free angle is particularly equivalent to the maximum movement angle of the rolling body relative to the clamping element holding body around the freewheel rotation axis, in particular the translation angle. The clamping element holding body load angle is in particular the sum of the mechanical clamping element holding body load angle and the chemical and / or thermal clamping element holding body load angle. The clamping element holding body load angle is preferably a maximum of 1°. It is particularly preferred that the clamping element holding body load angle is substantially 0.8°. However, it is also conceivable that the clamping element holding body load angle is greater than 1°. The mechanical clamping element holding body load angle is particularly related to possible mechanical deformations associated with the clamping element holding body during the operation of the clamping element unit. The mechanical clamping element holding body load angle is preferably a maximum of 0.7°. Particularly preferably, the mechanical clamping element holding body load angle is substantially 0.5°. However, it is also conceivable as an alternative that the mechanical clamping element holding body load angle is greater than 0.7°. The chemical and / or thermal clamping element holding body load angle is particularly related to possible thermal expansion of the clamping element holding body, possible material expansion (for example due to moisture absorption) or similar situations. The chemical and / or thermal clamping element holding body load angle is preferably a maximum of 0.5°. Particularly preferably, the chemical and / or thermal clamping element holding body load angle is substantially 0.3°. However, it is also conceivable as an alternative that the value of the chemical and / or thermal clamping element holding body load angle is greater than 0.5°. The sleeve free angle preferably corresponds to the maximum angle between the clamping position of at least one rolling body and the maximum free rotation position of at least one rolling body. The sum of the sleeve free angle and the sleeve load angle particularly results in the sleeve angle. The sleeve angle is preferably a maximum of 6.5°, preferably a maximum of 3.5°. Particularly preferably, the sleeve angle is substantially 3.3°. However, alternatively, it is also conceivable that the sleeve angle is greater than 6.5°. The sleeve load angle is preferably at least related to possible deformation and / or expansion of the force transmission element, in particular the sleeve, preferably at least one clamping surface during operation of the clamping element unit. The sleeve load angle is preferably a maximum of 4°, preferably a maximum of 2°. Very particularly preferably, the sleeve load angle is at least substantially 2.5°. However, alternatively, it is also conceivable that the sleeve load angle has a value greater than 4°. The spring angle is in particular the sum of the spring free angle and the spring load angle. The spring angle is preferably a maximum of 0.1°. Particularly preferably, the spring angle is substantially 0.05°. However, alternatively, it is also conceivable that the spring angle is greater than 0.1°. The spring free angle particularly relates to possible clearance of the connection between the clamping element retaining body and the spring unit, in particular at least one spring element.The spring load angle is particularly related to a possible bending of the at least one spring element. The spring load angle is preferably a maximum of 0.1°. Particularly preferably, the spring load angle is substantially 0.05°. Alternatively, however, it is also conceivable that the spring load angle is greater than 1°. Advantageously, a particularly reliable functioning of the clamping element unit of the bidirectional freewheel can be achieved.

[0041] The preload unit is preferably configured to hold or bring the clamping element holder into at least one defined position relative to the force transmission element, in particular relative to the gap and / or relative to the friction unit. Preferably, the preload unit is configured to enable the bidirectional freewheel to be activated or deactivated, in particular when the shaft rotates backward relative to the forward rotational direction. Preferably, the preload unit defines a bidirectional position and a unidirectional position of the clamping element holder relative to the force transmission element, in particular relative to the gap and / or relative to the friction unit. In the bidirectional position, the clamping element holder is arranged relative to the gap in such a way that the clamping element, in particular the rolling element, is prevented from being clamped between the clamping surfaces when moving in the direction of the clamping surfaces due to the early stop of the clamping element on the wall of the limiting accommodation area of ​​the clamping element holder. In the bidirectional position of the clamping element holder, preferably when the shaft rotates backward relative to the forward rotational direction, the torque transmission between the force transmission element and the shaft is prevented. In the one-way position, the clamping element holder is arranged relative to the gap in such a way that the clamping element, in particular the rolling body, remains spaced apart from the wall of the limiting receiving area of ​​the clamping element holder when moving in the direction of the clamping surfaces, so that the clamping element can be clamped between the clamping surfaces. In the one-way position of the clamping element holder, preferably when the shaft rotates backwards relative to the forward rotational direction, a torque transmission can be carried out between the force transmission element and the shaft. The activation or deactivation of the bidirectional freewheel is preferably carried out by the movement of the force transmission element. The movement of the force transmission element to be carried out for activating or deactivating the bidirectional freewheel is particularly related to the operating state before the shaft changes to the backward rotation relative to the forward rotational direction.

[0042] The pretensioning unit is preferably arranged on the clamping element holder. The pretensioning unit is preferably supported on the force transmission element, the friction unit and / or the housing component for applying force to the clamping element holder. The pretensioning unit can be connected to the clamping element holder and / or the force transmission element, the friction unit or the housing component, in particular by material locking, in particular by welding, can be constructed as one piece, or can be fixed to these components by form locking and / or force locking. The pretensioning unit is preferably elastically constructed, for example due to the shape and / or material of the pretensioning unit. The pretensioning unit is designed in particular so that in at least one operating state of the drive device, the pretensioning unit resists the relative movement of the clamping element holder relative to the force transmission element and / or the friction unit.

[0043] The configuration according to the invention advantageously allows the bidirectional freewheel to be combined with the roller freewheel required in general, and in particular allows a choice between torque transmission and no torque transmission, depending on the situation, during the backward movement of the axle. In addition, the position of the clamping element can be determined in advance for advantageous multiple situations and / or operating changes. In particular, it is advantageous to produce few situations in which the position of the clamping element is unknown. In particular, the clamping element occupies a defined position during idling, immediately before the torque transmission, so that there is advantageously a minimal risk of slipping. In particular, the electric bicycle can advantageously be reliably prevented from rolling backwards on a slope, because the pretensioning unit has already established a force balance for the torque transmission and the clamping element is advantageously clamped early.

[0044] It is further proposed that the clamping element unit comprises at least one mechanical control unit, in particular as already mentioned, wherein the control unit comprises a friction unit, in particular as already mentioned, which is arranged to generate an adjustment force, in particular as already mentioned, and the control unit comprises the at least one preload unit. The preload force is preferably an additional force in addition to the adjustment force. Preferably, the adjustment force and the preload force act together to bring and / or maintain the clamping element holding body in a defined position. Preferably, the preload force and the adjustment force have different points of action on the clamping element holding body. Preferably, the preload force is arranged to modify the adjustment force, in particular to make it direction-dependent. The adjustment force itself is typically non-direction-specific as a friction force. The preload force is preferably arranged to support the adjustment force in a reinforcing direction and to weaken the adjustment force in a suppressing direction. The reinforcing direction is, for example, at least substantially parallel or antiparallel to the forward rotation direction. The suppressing direction is, for example, at least substantially antiparallel or parallel to the forward rotation direction. By means of the configuration according to the invention, the position of the clamping element and / or the clamping element holding body can be advantageously and reliably determined when switching between different operating states of the drive device.

[0045] It is further proposed that the friction unit and the preload unit are arranged in such a way that the adjustment direction of the friction unit and the direction of action of the preload force are preferably oriented crosswise, in particular at least substantially perpendicularly. The adjustment direction is preferably predetermined by the spring unit of the friction unit. The adjustment direction preferably extends at least substantially perpendicularly to the adjustment force, in particular at least substantially parallel to the radial direction of the drive device. The direction of action of the preload force is preferably at least substantially parallel to or tangential to the circumferential direction. Preferably, the preload unit is constructed and / or arranged separately, differently and in particular at a distance from the spring unit. Through the configuration according to the present invention, the preload unit can advantageously be kept compact and can in particular be advantageously designed to be precisely coordinated with the adjustment force.

[0046] It is further proposed that the pretensioning unit has at least one spring element. Preferably, the pretensioning unit includes a plurality of spring elements, in particular at least two spring elements. The pretensioning unit includes a spring element in particular for each or every two spring elements of the friction unit. Alternatively, the number of spring units of the friction unit and the number of spring elements of the pretensioning unit are different. The spring elements of the pretensioning unit are preferably arranged at different, in particular evenly distributed points of action of the clamping element retaining body in the circumferential direction. In particular, the drive device is constructed rotationally symmetrically with respect to the spring elements of the pretensioning unit. Alternatively, the pretensioning unit includes exactly one spring element, or the spring elements are arranged at points of action of the clamping element retaining body that are unevenly distributed in the circumferential direction. The spring elements of the pretensioning unit are preferably constructed to be identical in structure. Alternatively, the pretensioning unit includes at least two differently constructed spring elements. The pretensioning unit can be advantageously realized in a simple and sturdy manner through the configuration scheme according to the present invention.

[0047] It is further proposed that at least one spring element is configured as a compression spring. The compression spring is configured as a cylinder, a cone, a barrel, a waist or an arch. The spring travel of the compression spring is preferably at least substantially parallel to or tangential to the circumferential orientation. Alternatively, the spring travel has an angle greater than 10°, but preferably at least less than 45°. The compression spring is preferably arranged at the radial outward turn of the clamping element retaining body. The compression spring is preferably supported on the force transmission unit and / or the housing component. The configuration according to the present invention can advantageously keep the preload unit compact.

[0048] It is further proposed that the at least one spring element or another spring element of the preload unit is configured as a leaf spring. The leaf spring preferably comprises a support body and a spring leaf protruding from the support body. The support body is, for example, similar to the support body structure of the spring unit of the friction unit, on which two spring elements of the spring unit are particularly arranged. Preferably, the support body is fixed to the clamping element holding body, in particular, is overmolded by the clamping element holding body, or is integrally configured with the clamping element holding body. The support body preferably has a main extension plane at least substantially parallel to the radial direction. Preferably, the spring leaf is arranged on the end of the support body that faces away from the clamping element holding body in the radial direction and extends from there in the direction of the clamping element holding body. The spring leaf is preferably arranged between the support body and the force transmission element and / or the housing component in the circumferential direction. The spring leaf preferably has a folded portion in the direction of the support body on the end facing the clamping element holding body. Preferably, the folded portion is arranged in at least one operating state of the drive device for hitting against the force transmission element and / or the housing component. By the configuration according to the present invention, the drive device is advantageously kept to be easily assembled.

[0049] It is further proposed that the preload unit and the friction unit are arranged in the same receiving area of ​​the control unit, in particular the clamping element holder already mentioned. Preferably, the clamping element holder has at least one assembly structural element, on which the control unit and / or the preload unit are arranged. The clamping element holder preferably comprises an annular base body, in which a plurality of receiving areas are arranged. The assembly structural element preferably extends in a manner that departs from the annular base body in a radial direction. The assembly structural element can be constructed as a receiving portion, in particular a bushing, as a continuation, as a guide rail, as a welding surface or as other structures that the technician considers useful, so that the control unit and / or the preload unit are arranged on, in particular fixed to, the clamping element holder. The clamping element holder preferably comprises a plurality of assembly structures, in particular structurally identical, which are preferably regularly, in particular rotationally symmetrically arranged circumferentially on the annular base body. The assembly structure can extend circumferentially over just one or more receiving areas. “The pretensioning unit and the friction unit are arranged in the same receiving area” should be understood in particular to mean that the pretensioning unit and the friction unit are arranged on the same mounting structure, in particular regardless of how many receiving areas the mounting structure extends over. Preferably, the friction unit and / or the pretensioning unit comprises a plurality of separate identical components, each of which in particular has at least one spring element, and which are distributed on different mounting structures. Preferably, the friction unit and the pretensioning unit each comprise at least one component, which is arranged on the same mounting structure. Preferably, in particular when the pretensioning unit is configured with a compression spring, a component of the friction unit is arranged on each mounting structure. Preferably, in particular when the pretensioning unit is configured with at least one compression spring, a component of the pretensioning unit is additionally arranged on at least one, in particular each, of the mounting structures. The configuration according to the invention can advantageously achieve a uniformly distributed, in particular rotationally symmetrical, force action on the base body of the clamping element. In particular, the risk of imbalance of the drive device can advantageously be kept to a minimum.

[0050] It is further proposed that the pretensioning unit and the friction unit are arranged on different receiving areas of the control unit, in particular the clamping element holding body already mentioned. Preferably, in particular when the pretensioning unit is constructed with at least one leaf spring, either a component of the friction unit or a component of the pretensioning unit is arranged on at least one, in particular each mounting structure. In a specific configuration, the pretensioning unit comprises a component of a leaf spring, which is located on one of the mounting structures, on which in particular no friction unit component is arranged, and has at least one component with a compression spring, which is located on at least one other mounting structure of the mounting structure, on which the friction unit component is also arranged. The number of mounting structures with friction unit components and in particular without pretensioning unit components and the number of mounting structures with pretensioning unit components and in particular without friction unit components can be of equal or different size. The configuration according to the invention advantageously allows a simple assembly of the drive device.

[0051] Furthermore, a drive unit for an electric bicycle is proposed, which has a drive device according to the invention. The drive device is arranged in particular at least partially, preferably at least mostly, inside the housing of the drive unit. Preferably, the electric motor and / or the transmission are arranged at least mostly inside the housing. Advantageously, a particularly strong and / or durable drive unit can be provided. Advantageously, the drive unit can be operated particularly gently.

[0052] An electric bicycle is also proposed with a drive unit according to the invention. The drive unit, in particular the housing of the drive unit, is preferably fastened to the frame of the electric bicycle. The electric bicycle preferably comprises a winding device. It is conceivable that at least the housing of the drive unit is at least partially constructed in one piece with at least a part of the frame. Advantageously, an electric bicycle with a particularly responsive bidirectional freewheel can be provided. Advantageously, a particularly precise driving behavior, in particular a driving behavior, can be achieved.

[0053] 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 to be restricted to the above-described applications and embodiments. The drive device according to the invention, the drive unit according to the invention and / or the electric bicycle according to the invention may have a number of individual elements, components and units that differs from the number mentioned here, in particular to fulfill the functional mode described here. Furthermore, within the numerical ranges specified in the disclosure, values ​​that lie within the mentioned boundaries are also to be regarded as disclosed and may be used arbitrarily. BRIEF DESCRIPTION OF THE DRAWINGS

[0054] Further advantages are derived from the following description of the drawings. Two embodiments of the present invention are shown in the drawings. The drawings, the description and the technical solution contain a plurality of feature combinations. A person skilled in the art can also consider these features individually and combine them into other meaningful combinations in accordance with the purpose.

[0055] In the attached figure:

[0056] Figure 1 : A schematic diagram is used to describe an electric bicycle according to the invention having a drive unit according to the invention,

[0057] Figure 2 : A simplified schematic diagram of a drive device according to the invention showing a drive unit,

[0058] Figure 3 : A driving unit is shown in a three-dimensional cross-sectional view,

[0059] Figure 4 : A driving device is shown in a three-dimensional diagram,

[0060] Figure 5 : The drive device is shown in an exploded view,

[0061] Figure 6 : Shows the spring element of the drive device and

[0062] Figure 7 : A schematic diagram shows a portion of the drive device of the present invention in an alternative embodiment. DETAILED DESCRIPTION

[0063] Figure 1 An electric bicycle 14a is shown. The electric bicycle 14a has a frame 68a. The electric bicycle 14a includes a drive unit 12a. The drive unit 12a is arranged on the frame 68a. The drive unit 12a is arranged in a pedal bearing area 70a of the electric bicycle 14a. The drive unit 12a includes a housing 72a (see Figure 3 ). The drive unit 12a includes an electric motor 74a. The drive unit 12a includes a transmission device 76a for transmitting the driving force of the drive unit 12a, in particular the electric motor 74a, to the driven pinion 108 of the drive unit 12a. The driven pinion 108a is configured as a sprocket or the like. The driven pinion 108a is connected to the transmission device output end of the transmission device 76a.

[0064] The drive unit 12a comprises at least one drive device 10a. The drive device 10a is arranged at least partially, preferably at least mostly, inside the housing 72a. Figure 2The structure of the drive device 10a is shown in a simplified schematic diagram. The drive device 10a has a bidirectional freewheel 16a. The freewheel 16a is configured as a freewheel based on force locking. The freewheel 16a is configured differently from the pawl freewheel. The freewheel 16a has at least one clamping element unit 18a. The clamping element unit 18a is configured as a clamping roller unit. However, it is conceivable that the clamping element unit 18a is configured as a clamping body unit or as a clamping ball unit. The clamping element unit 18a is arranged on the transmission output end of the drive unit 12a. It is also conceivable that the clamping element unit 18a is arranged at other positions inside the transmission 76a.

[0065] The drive unit 12a comprises at least one pedal crankshaft (not shown here). The pedal crankshaft can be driven by the user via the pedal. The driven pinion 108a is connected to the pedal crankshaft in such a way that the driven pinion 108a can be driven by the rotation of the pedal crankshaft, in particular at least in one rotational direction, preferably in the direction of the forward rotational direction 78a of the drive device 10a. The forward rotational direction 78a corresponds to the forward movement of the electric bicycle 14a. It is conceivable that the shaft 50a is connected to the pedal crankshaft in a rotatably supported manner. In addition, it is conceivable that the drive unit 12a has another freewheel (not shown here), which is arranged between the shaft 50a and the pedal crankshaft. The other freewheel is preferably arranged to prevent the pedal crankshaft from rotating together when the shaft 50a rotates. Alternatively, it is conceivable that the shaft 50a is connected to the pedal crankshaft in a rotationally fixed manner. In particular, it is conceivable that the shaft 50a is integrally constructed with the pedal crankshaft. It is also conceivable as an alternative that the shaft 50a corresponds to the pedal crank shaft.

[0066] The drive device 10a includes at least one force transmission element 42a for transmitting the driving force of the drive unit 12a. The clamping element unit 18a is arranged on the force transmission element 42a. The force transmission element 42a is configured as a spur gear. The spur gear has an external toothing. It is conceivable that the external toothing is configured as a straight toothing or a helical toothing. However, it is conceivable that the force transmission element 42a is configured as a planetary gear, a ring gear, a sun gear or other force transmission elements that professionals consider useful. The force transmission element 42a forms the transmission output of the drive unit 12a. However, it is conceivable that the force transmission element 42a is arranged inside the drive device 76a and is particularly configured to transmit force to the intermediate shaft of the transmission device 76a.

[0067] The drive device 10a comprises at least a shaft 50a. The shaft 50a is configured as a driven shaft. However, alternatively, it is conceivable that the shaft 50a is configured as an intermediate shaft or a similar structure, which is particularly arranged inside the transmission device 76a. The driven pinion 108a is connected to the shaft 50a in a rotationally fixed manner. It is conceivable that the driven pinion 108a is integrally configured with the shaft 50a.

[0068] The freewheel 16a has an axis of rotation 34a. The shaft 50a and the force transmission element 42a are arranged coaxially around the axis of rotation 34a (see Figure 3 , 4 and 5). The shaft 50a, the pedal crank shaft and / or the force transmission element 42a are rotatably arranged around the rotation axis 34a. By rotating the shaft 50a around the rotation axis 34a, a torque can be generated at the driven pinion 108a. The clamping element unit 18a is configured to interrupt the transmission of the motor torque pointing forward relative to the forward rotation direction of the electric bicycle 14a to the shaft 50a, in particular the driven pinion 108a, when the rotation speed of the shaft 50a is greater than the rotation speed of the force transmission element 42a driven by the motor torque. The clamping element unit 18a is configured to interrupt the transmission of the motor torque pointing backward relative to the forward rotation direction of the electric bicycle 14a to the shaft 50a, in particular the driven pinion 108a, when the rotation speed of the shaft 50a, in particular the driven pinion 108a, is greater than the rotation speed of the force transmission element 42a driven by the motor torque. The clamping element unit 18a is designed 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 force transmission element 42a, preferably the gear 76a and / or the motor 74a, when the shaft 50a, in particular the output pinion 108a, rotates backward relative to the forward rotational direction 78a. The clamping element unit 18a is designed 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 force transmission element 42a, preferably the gear 76a and / or the motor 74a, independently of the rotational speed of the force transmission element 42a and independently of the rotational speed of the shaft 50a, in particular the output pinion 108a.

[0069] The clamping element unit 18a is provided for decoupling the vibration of the winding means 58a. The winding means 58a is configured as a chain. Alternatively, it is also conceivable that the winding means 58a is configured as a drive belt or the like. The winding means 58a is preferably connected to the driven shaft, in particular the driven pinion 108, in a rotationally fixed manner. The winding means 58a is provided for transmitting the driving force from the shaft 50a, in particular from the driven pinion 108a, to the drive wheel 80a of the electric bicycle 14a. The drive wheel 80a is configured as the rear wheel of the electric bicycle 14a. However, it is alternatively conceivable that the drive wheel 80a is configured as the front wheel of the electric bicycle 14a. The clamping element unit 18a is provided for counteracting the transmission of the vibration of the winding means 58a to a component of the drive unit 12a that is arranged behind the clamping element unit 18a in the drive train starting from the winding means 58a. The clamping element unit 18a is provided for counteracting the transmission of the vibration of the winding means 58a to the transmission device 76a and / or the electric motor 74a.

[0070] The clamping element unit 18a includes a plurality of rolling bodies 20a (in Figure 2 Only one rolling body 20a is shown in the simplified schematic diagram in FIG. 1 . It is also conceivable that the clamping element unit 18a includes only one rolling body 20a. The rolling body 20a is configured as a roller. Alternatively, it is also conceivable that the rolling body 20a is configured as a ball, a barrel, a needle, a cone or other rotating bodies that are considered useful by professionals. The rolling body 20a is configured to transmit torque between the force transmission element 42a and the shaft 50a when the rolling body 20a is in the clamping position. The rolling body 20a is configured to interrupt the torque transmission between the force transmission element 42a and the shaft 50a when the rolling body 20a is in the free rotation position.

[0071] 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 integrally formed with the force transmission element 42a. It is conceivable that the sleeve 40a is formed by the force transmission element 42a. The rolling bodies 20a are arranged between the force transmission element 42a, in particular the sleeve 40a, and the shaft 50a. The rolling bodies 20a are arranged uniformly. The rolling bodies 20a are arranged uniformly along the circumferential direction of the shaft 50a, which extends in particular in a plane perpendicular to the rotation axis 34a.

[0072] The clamping element unit 18a has at least one clamping surface 82a, preferably a plurality of clamping surfaces 82a. The sleeve 40a has at least one clamping surface 82a. The clamping surface 82a is provided for cooperating with at least one rolling body 20a to transmit torque between the force transmission element 42a and the shaft 50a. The clamping element unit 18a has at least one additional clamping surface 84a. The additional clamping surface 84a is provided for cooperating with at least one rolling body 20a to transmit torque between the force transmission element 42a and the shaft 50a. The shaft 50a has a cylindrical outer peripheral surface 86a. The additional clamping surface 84a is formed by the cylindrical outer peripheral 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 the clamping surfaces 82a corresponds to the number of the rolling bodies 20a. A clamping surface 82a is associated with each of the rolling elements 20a.

[0073] The rolling bodies 20a are each provided for clamping with one of the clamping surface 82a and the further clamping surface 84a for transmitting torque between the force transmission element 42a and the shaft 50a. The sleeve 40a has at least a plurality of recesses 90a (in Figure 22 ). Only one gap 90a is shown in a simplified schematic diagram. The number of gaps 90a corresponds to the number of rolling bodies 20a. One of the clamping surfaces 82a is arranged in each gap 90a. The gap 90a is designed asymmetrically, in particular at least when viewed in the circumferential direction of the force transmission element 42a, which is preferably in a plane extending perpendicular to the rotation axis 34a. The gap 90a is designed in such a way that the rolling body 20a can be arranged in the gap 90a in a clamped position at the clamping surface 82a or in a freely rotating position.

[0074] The clamping element unit 18a comprises at least one clamping element holding body 36a (in Figure 2 The clamping element holding body 36a is schematically and simplified in the figure. The clamping element holding body 36a has a plurality of receiving areas 92a for rolling bodies 20a. The clamping element holding body 36a is annular in structure (see Figure 4 and 5 ). The clamping element retaining body 36a is constructed as a cage ring. The number of accommodating areas 92a corresponds to the number of rolling bodies 20a. The accommodating areas 92a are separated from each other. The accommodating areas 92a limit the movement of the rolling bodies 20a relative to the clamping element retaining body 36a, in particular the movement around the axis of rotation 34a, preferably in the circumferential direction. The clamping element retaining body 36a is arranged between the shaft 50a and the force transmission element 42a, in particular the sleeve 40a. The clamping element retaining body 36a is movably arranged relative to the force transmission element 42a (in particular the sleeve 40a) and / or the shaft 50a. The clamping element retaining body 36a is configured to guide the rolling bodies 20a.

[0075] The clamping element unit 18a comprises a mechanical control unit 22a. The control unit 22a is configured to switch the freewheel 16a between an idling state and a torque transmission state. The idling state is a state of the freewheel 16a in which the torque transmission between the force transmission element 42a and the shaft 50a is interrupted. The torque transmission state is a state of the freewheel 16a in which a torque transmission takes place between the force transmission element 42a and the shaft 50a. The switch between the idling state and the torque transmission state takes place automatically with the aid of the control unit 22a, in particular without user intervention and / or without electrical control. The control unit 22a has no electrical components. However, it is alternatively conceivable that the clamping element unit 18a comprises an electrical control unit.

[0076] The control unit 22a has a friction unit 24a which is provided for generating an adjustment force. The friction unit 24a is provided for moving the clamping element holder 36a relative to the force transmission element 42a and / or the shaft 50a, in particular rotating it about the rotation axis 34a. The friction unit 24a is provided at least for releasing the torque transmission state of the freewheel 16a as a function of a relative movement of the force transmission element 42a relative 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 16a freewheel state by means of an adjustment force as a function of a relative movement of the force transmission element 42a relative to 50a. The friction unit 24a is provided for positioning the rolling element 20a relative to the force transmission element 42a, in particular the sleeve 40a, and / or the shaft 50a, preferably around the freewheel 16a, preferably at least from the torque transmission state to the freewheel state.

[0077] The friction unit 24a is configured to generate a friction force between the clamping element retaining body 36a and a friction body 94a that is constructed separately from the clamping element retaining body 36a. The friction body 94a is a stationary component of the freewheel 16a. The friction body 94a is constructed as a friction ring. The friction body 94a is connected to the housing component 62a of the housing 72a in a rotationally fixed manner. Alternatively, it is also conceivable that the friction body 94a is formed by a stationary component of the electric bicycle 14a, in particular the drive unit 12a. The friction body 94a is alternatively constructed, for example, by the housing component 62a, by a frame element of the frame 68a, or by a similar component. A friction contact is formed between the clamping element retaining body 36a and the friction body 94a by the friction unit 24a. The friction unit 24a has a plurality of friction elements 66a (in Figure 2 Only two friction elements 66a are shown in the simplified schematic diagram of FIG. 2 . The friction unit 24a has four friction elements 66a. Alternatively, it is also conceivable that the friction unit 24a has a number of friction elements 66a 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 arranged to form a friction contact between the clamping element retaining body 36a and the friction body 94a. The friction elements 66a are arranged along the circumferential direction of the clamping element retaining body 36a, and the circumferential direction extends in particular in a plane perpendicular to the rotation axis 34a.

[0078] The friction elements 66a each have two friction surfaces 38a for forming friction contact between the clamping element holder 36a and the friction body 94a. Alternatively, it is also conceivable that the friction elements 66a each have only one friction surface 38a or more than two friction surfaces 38a. However, it is also conceivable that the friction elements 66a are arranged unevenly in the circumferential direction, preferably on the clamping element holder 36a or the friction body 94a. The friction element 66a is fixed on the clamping element holder 36a. The friction element 66a is integrally constructed with the clamping element holder 36a.

[0079] The adjusting force is a friction force. The friction unit 24a is provided to generate an adjusting force between the clamping element holder 36a and the friction body 94a by static friction and / or sliding friction in at least one operating state of the freewheel 16a. The adjusting force, in particular the friction force, at least in the operating state of the freewheel 16a, counteracts a torque applied to the clamping element holder 36a. The adjusting force, preferably the friction force, is provided to delay a rotation of the clamping element holder 36a about the rotation axis 34a relative to the shaft 50a, in particular at least in the idling state.

[0080] The drive device 10a comprises at least one bearing unit 96a (see Figure 3 ), which is at least partially arranged between the force transmission element 42a (especially the sleeve 40a) and the shaft 50a. The bearing unit 96a is at least configured to support the force transmission element 42a and the shaft 50a rotatably relative to each other and / or at a fixed radial distance from each other. The bearing unit 96a includes at least two bearing elements 54a. Alternatively, it is also conceivable that the bearing unit 96a includes only one bearing element 54a or includes more than two bearing elements 54a. The bearing element 54a is configured as a sliding bearing ring. The bearing element 54a is arranged between the force transmission element 42a (especially the sleeve 40a) and the shaft 50a.

[0081] The clamping element unit 18a is designed to clamp the rolling elements 20a in the recess 90a by means of the respective clamping surfaces 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 the rotational speed of the force transmission element 42a is greater than the rotational speed of the shaft 50a, the friction unit 24a is designed to brake the clamping element holding body 36a relative to the force transmission element 42a by means of an adjustment force, in particular a friction force, so that the rolling elements 20a come into contact with the clamping surfaces 82a in the recess 90a of the sleeve 40a and are clamped. The clamping element unit 18a is designed to generate a force acting on the rolling elements 20a by means of an adjustment force, in particular a friction force, when the rotational direction of the shaft 50a points backward relative to the forward rotational direction 78a, so that the rolling elements 20a disengage from the clamping surfaces 82a, so that the freewheel 16a switches to the freewheeling state. Preferably, at least when the rotation of the force transmission element 42 is directed forward relative to the forward rotation direction 78a, when the rotation speed of the force transmission element 42a is greater than the rotation speed of the shaft 50a, a clamping of the rolling elements 20a with the force transmission element 42a, in particular the sleeve 40a, and the shaft 50a can be generated by adjusting the force, in particular the friction force. 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.

[0082] The rolling body 20a is connected to the force transmission element 42a (especially the sleeve 40a) and the shaft 50a in a torque transmission state. When the freewheel 16a is in the torque transmission state, the rolling body 20a is in particular in the clamping position. The rolling body 20a is arranged in the free rotation in the freewheel state. When the freewheel 16a is in the freewheel state, the rolling body 20a is in particular in a free rotation position. When the shaft 50a rotates backward relative to the forward rotation direction 78a, the rolling body 20a is respectively arranged in the free rotation in the gap 90a. When the shaft 50a rotates forward relative to the forward rotation direction 78a and the rotation speed of the shaft 50a is greater than the rotation speed of the force transmission element 42a, the rolling body 20a is respectively arranged in the free rotation in the gap 90a. When the force transmission element 42a rotates backward relative to the forward rotation direction 78a, the rolling body 20a is respectively arranged in the free rotation in the gap 90a. The clamping element unit 18a is provided to release the clamping of the rolling elements 20a by means of the clamping element holder 36a when the rotational speed of the shaft 50a is greater than the rotational speed of the force transmission element 42a.

[0083] The clamping element unit 18a includes at least one pretensioning unit 112a which is configured to generate a pretensioning force. The control unit 22a includes at least one pretensioning unit 112a in addition to the friction unit 24a. The friction unit 24a and the pretensioning unit 112a are arranged so that the adjustment direction of the friction unit 24 and the direction of action of the pretensioning force are preferably oriented crosswise, in particular at least substantially perpendicularly. The pretensioning unit 112a is preferably arranged on the clamping element holding body 36a. The pretensioning unit 112a is arranged, for example, on the force transmission element 42a. The pretensioning unit 112a preferably includes at least one spring element 114a, which acts on the clamping element holding body 36a along or against the forward rotation direction 78a to apply a spring force. The spring element 114a acts on the clamping element holding body 36a in the circumferential direction, preferably on the side facing the gap 90a, in particular on the side of the sleeve 40a facing away from the clamping surface 82a.

[0084] The clamping unit 24a comprises at least one spring unit 26a. The clamping element holder 36a is connected to the friction body 94a via the spring unit 26a. The spring unit 26a is configured to generate a holding force between the clamping element holder 36a and the friction body 94a. The spring unit 26a is configured to generate an adjustment force, in particular a friction force, of the friction unit 24a. The spring unit 26a has four spring elements 32a (see Figure 4 and 5 ). However, alternatively, it is also conceivable that the spring unit 26a has a number of spring elements 32a 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 unit 66a is formed by the spring element 32a. The spring element 32a is configured as a bending spring 28a. Alternatively, it is also conceivable that the spring element 32a is configured as a torsion spring, a disc spring, a spiral spring, an annular spring or a similar spring. Alternatively, it is also conceivable that the spring element 32a is configured as a rubber elastic element. The spring element 32a is arranged on the clamping element retaining body 36a. The spring element 32a is arranged between the clamping element retaining body 36a and the friction body 94a. The clamping element retaining body 36a is connected to the friction body 94a via the spring element 32a. The four spring units 32a each have two assembly ramps 60a (see Figure 6 The mounting ramp 60a is formed by a surface which extends at an angle, preferably in a direction different from vertical, to the rotation axis 34a.

[0085] The bending spring 28a is designed as a leaf spring 30a. Alternatively, it is also conceivable that the bending spring 28a is designed as a wire spring, a needle spring, a helical torsion spring or the like. Preferably, the spring unit 26a is designed without a helical spring. The leaf spring 30a is designed as a leaf spring with at least two wings. However, it is also conceivable that the leaf spring 30a is designed as a single-wing leaf spring, a helical spring, a buffer spring elliptical spring, a parabolic spring, a wave spring or other leaf springs that the skilled person considers useful. The leaf spring 30a has two spring wings (see Figure 6 ). The friction surfaces 38a of the friction elements 66a are respectively arranged on the spring wings 56a.

[0086] The rolling body 20a is arranged on the clamping element holding body 36a without a spring. The receiving area 92a for the rolling body 20a has no spring element. In particular, the area between the rolling body 20a and the clamping element holding body 36a is preferably free of spring elements at least in the corresponding receiving area 92a. The rolling body 20a is not supported on the clamping element holding body 36a by means of a spring element.

[0087] The spring element 32a is fixed on the clamping element holding body 36a. The spring element 32a is made of a material different from the material used to form the clamping element holding body 36a. The spring element 32a is formed of metal. However, it is also conceivable that the spring element 32a is formed of plastic or other materials that are considered useful by the technician. The clamping element holding body 36a is formed of plastic. However, it is also conceivable that the clamping element holding body 36a is formed of metal or other materials that are considered useful by the technician. However, it is also conceivable that the spring element 32a and the clamping element holding body 36a are constructed of the same material. The spring element 32a is integrally constructed with the clamping element holding body 36a. The spring element 32a is overmolded by the clamping element holding body 36a. The spring element 32a is at least partially overmolded by the clamping element holding body 36a.

[0088] The spring element 32a has two connecting elements 106a respectively, which are used to connect the spring element 32a to the clamping element holding body 36a. The connecting element 106a is configured as an opening. However, it is also conceivable that the connecting element 106a is configured as other connecting elements 106a that the technician finds useful. The connecting element 106a is configured to be injection-molded through the clamping element holding body 36a when manufacturing the clamping element unit 18a. The spring element 32a has an assembly element 104a respectively. Each assembly element 104a is configured to support the spring element 32a to be arranged in an assembly position on the clamping element holding body 36a before overmolding. The assembly element 104a is configured as an opening. However, it is also conceivable that the assembly element 104a is configured as a protrusion or other assembly element 104a that the technician finds useful.

[0089] The friction surface 38a of the friction unit 24a, in particular the friction element 66a, extends in the axial direction. The axial direction extends parallel to the axis of rotation 34a. The friction surface 38a is at least partially curved. Alternatively or additionally, it is conceivable that the friction surface 38a extends at least partially straight. The friction surfaces 38a each have a main extension plane, which extends at least substantially parallel to the axial direction.

[0090] The friction surface 38a extending in the axial direction is arranged on the side facing away from the clamping element holding body 36a when viewed in the axial direction. In particular, at least when viewed in the axial direction, the spring wing 56a of the spring element 32a is arranged on the side facing away from the clamping element holding body 36a. The friction surface 38a extending in the axial direction is oriented inwardly when viewed in the radial direction. The friction surface 38a is arranged to face the shaft 50a. The friction surface 38a is arranged to face the rotation axis 34a.

[0091] The force transmission element 42a has four through-holes 44a, through which the individual assembly structures of the clamping element holding body 36a are respectively led outwards at least partially in the radial direction. Alternatively, it is also conceivable that the force transmission element 42a has a number of through-holes 44a different from four, for example only one through-hole 44a, two, three or more than four through-holes 44a. The number of through-holes 44a corresponds in particular to the number of friction elements 66a, in particular spring elements 32a. However, it is also conceivable that the number of through-holes 44a is different from the number of friction elements 66a, in particular spring elements 32a.

[0092] The mounting structure of the clamping element holding body 36a is configured as a receiving portion, for example, which receives the spring element 32a of the spring unit 26a. The mounting structure is completed in particular by overmolding of the spring element 32a. The pretensioning unit 112a and the friction unit 24a are arranged on the same mounting structure of the clamping element holding body 36a. In particular, at least one spring element 32a of the friction unit 24a and a spring element 114a, 116a of the pretensioning device 112a are arranged on each mounting structure of the clamping element holding body 36a. The pretensioning unit 112a preferably includes at least one, in particular exactly one, for example four spring elements 114a, 116a for each through-portion 44a, and two of these spring elements are provided with marking symbols. The spring elements 114a, 116a of the pretensioning unit 112a are configured as compression springs. The spring elements 114a, 116a are arranged, for example, in the aperture 44a and are supported in particular on a wall delimiting the aperture 44a in the circumferential direction. The spring elements 114a, 116a act on the clamping element holder 36a in the circumferential direction, preferably on a respective mounting structure.

[0093] The maximum diameter 46a of the rolling element 20a has a value between 6% and 20% of the value of the maximum inner diameter 48a of the force transmission element 42a, in particular the sleeve 40a. Preferably, the maximum diameter 46a of the rolling element 20a has a value of at most 15%, particularly preferably at most 10%, of the value of the maximum inner diameter 48a of the force transmission element 42a, in particular the sleeve 40a. Alternatively, however, it is also conceivable that the maximum diameter 46a of the rolling element 20a has a value outside the range between 6% and 20% of the value of the maximum inner diameter 48a of the force transmission element 42a, in particular 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. The maximum diameter 46a of the rolling element 20a has a value between 8% and 25% of the value of the maximum diameter 52a of the shaft 50a. Preferably, the maximum diameter 46a of the rolling element 20a has a value of at most 15%, particularly preferably at most 12% of the value of the maximum diameter 52a of the shaft 50a. Alternatively, however, it is also conceivable that the value of the maximum diameter 46a of the rolling element 20a lies outside the range between 8% and 25% of the 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.

[0094] The value of the maximum diameter 52a of the shaft 50a is, for example, a maximum of 38 mm, and the value of the maximum diameter 52a of the shaft 50a is particularly preferably 32 mm. The value of the maximum inner diameter 48a of the force transmission element 42a (especially the sleeve 40a) is a maximum of 45 mm. Preferably, the value of the maximum inner diameter 48a of the force transmission element 42a (especially the sleeve 40a) is between 40 mm and 41 mm. However, it is also conceivable as an alternative that the value of the maximum inner diameter 48a of the force transmission element 42a (especially the sleeve 40a) is greater than 45 mm. The value of the maximum diameter 46a of the rolling body 20a is a maximum of 5 mm. Preferably, the value of the maximum diameter 46a of the rolling body 20a is substantially 3.5 mm. However, it is also conceivable as an alternative that the value of the maximum diameter 46a of the rolling body 20a is greater than 5 mm.

[0095] The maximum movement angle, in particular the translation angle, of the rolling bodies 20a relative to the clamping element holder 36a about the rotation axis 34a of the freewheel 16a is at most 1.5°. Preferably, the maximum movement angle, in particular the translation angle, of the rolling bodies 20a relative to the clamping element holder 36a is between 0° and 1°. Particularly preferably, the maximum movement angle, in particular the translation angle, of the rolling bodies 20a relative to the clamping element holder 36a is substantially 0.5°. Alternatively, however, it is also conceivable that the maximum movement angle, in particular the translation angle, of the rolling bodies 20a relative to the clamping element holder 36a about the rotation axis 34a is greater than 1.5°.

[0096] The maximum angle between the respective clamping position of the rolling body 20a and the respective maximum free rotation position of the rolling body 20a about the rotation axis 34a of the freewheel 16a is at most 5°. Preferably, the maximum angle between the respective clamping position of the rolling body 20a and the respective maximum free rotation position of the rolling body 20a about the rotation axis 34a of the freewheel 16a is at most 2.5°. Preferably, the maximum angle between the respective clamping position of the rolling body 20a and the respective maximum free rotation position of the rolling body 20a about the rotation axis 34a of the freewheel 16a is between 0.3° and 2.5°, particularly preferably between 0.4° and 2°. Very particularly preferably, the maximum angle between the respective clamping position of the rolling body 20a and the respective maximum rotation position of the rolling body 20a freely about the rotation axis 34a of the freewheel 16a is at least substantially 0.8°. The respective maximum free rotation position of the rolling body 20a and the respective clamping position are each located in one of the recesses 90a for the rolling body 20a. The respective maximum free rotation positions and clamping positions are located at mutually opposite end regions of the gap 90a. The clamping surfaces 82a are respectively arranged on the rear side of the gap 90a relative to the forward rotation direction 78a. The respective free rotation positions are arranged on the front side of the gap 90a relative to the forward rotation direction 78a. The gap 90a has a stop for the corresponding rolling body 20a in the end region where the free rotation position of the respective, in particular corresponding rolling body 20a is located. Alternatively, it is also conceivable that the maximum angle between the respective clamping position of the rolling body 20a and the respective maximum free rotation position about the rotation axis 34a of the freewheel 16a is greater than 5°. When the rolling body 20a is in contact with the corresponding stop of the gap 90a, the rolling body 20a is respectively in the maximum free rotation position.

[0097] The clamping element unit 18a and the force transmission element 42a have a common cross section extending at least substantially perpendicular to the rotation axis 34a. The clamping element unit 18a is arranged at least substantially completely inside the force transmission element 42a. Alternatively, it is also conceivable that the clamping element unit 18a is arranged offset in the axial direction relative to the force transmission element 42a so that at least the external toothing of the force transmission element 42a and the clamping element unit 18a do not have a common cross section extending at least substantially perpendicular to the rotation axis 34a.

[0098] The sum of the cage angle and the spring angle is less than or equal to the sleeve free angle. The clamping element retaining body angle is formed by the sum of the clamping unit retaining body free angle and the clamping element retaining body load angle. The clamping element retaining body angle is a maximum of 2.5°. Particularly preferably, the clamping element retaining body angle is substantially 1.8°. However, alternatively, it is conceivable that the clamping element retaining body angle is greater than 2.5°. The clamping unit retaining body free angle corresponds to the maximum movement angle, in particular the translation angle, of the rolling body 20a relative to the rotation angle 34a of the clamping element retaining body 36a around the free wheel 16a. The clamping element retaining body load angle is the sum of the mechanical clamping element retaining body load angle and the chemical and / or thermal clamping element retaining body load angle. The clamping element retaining body load angle is a maximum of 1°. Particularly preferably, the clamping element retaining body load angle is substantially 0.8°. However, alternatively, it is conceivable that the clamping element retaining body load angle is greater than 1°. The mechanical clamping element holding body load angle is particularly related to possible mechanical deformations associated with the clamping element holding body 36a during the operation of the clamping element unit 18a. The mechanical clamping element holding body load angle is a maximum of 0.7°. It is particularly preferred that the mechanical clamping element holding body load angle is substantially 0.5°. However, it is alternatively conceivable that the value of the mechanical clamping element holding body load angle is greater than 0.7°. The chemical and / or thermal clamping element holding body load angle is particularly related to possible thermal expansion, possible material expansion (for example caused by moisture absorption) of the clamping element holding body 36a or similar situations. The chemical and / or thermal clamping element holding body load angle is a maximum of 0.5°. It is particularly preferred that the chemical and / or thermal clamping element holding body load angle is substantially 0.3°. However, it is also conceivable that the chemical and / or thermal clamping element holding body load angle is greater than 0.5°.

[0099] The sleeve free angle preferably corresponds to the corresponding maximum angle between the respective clamping position of the rolling body 20a and the respective maximum free rotation position of the rolling body 20a. The sum of the sleeve free angle and the sleeve load angle in particular results in the 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°. However, alternatively, it is conceivable that the sleeve angle is greater than 6.5°. The sleeve load angle is preferably at least related to the possible deformation and / or expansion of the force transmission element 42a, in particular the sleeve 40a, preferably the clamping surface 82a during the operation of the clamping element unit 18a. The sleeve load angle is a maximum of 4°, preferably a maximum of 2°. It is particularly preferred that the sleeve load angle is at least substantially 2.5°. However, alternatively, it is also conceivable that the sleeve load angle has a value greater than 4°. The spring angle is in particular the sum of the spring free angle and the spring load angle. The spring angle is a maximum of 0.1°. Particularly preferably, the spring angle is substantially 0.05°. However, alternatively, it is also conceivable that the spring angle is greater than 0.1°. The spring free angle relates in particular to a possible play of the connection between the clamping element holder 36a and the spring unit 26a, in particular the spring element 32a. The spring load angle is in particular related to a possible bending of the corresponding spring element 32a. The spring load angle is preferably a maximum of 0.1°. Particularly preferably, the spring load angle is substantially 0.05°. Alternatively, however, it is conceivable that the spring load angle is greater than 1°. The freewheel function angle is in particular the sum of the sleeve angle, the clamping element holder angle and the spring angle.

[0100] exist Figure 7 Another embodiment of the present invention is shown in FIG. The following description and drawings are essentially limited to the differences between the embodiments, wherein, for components with the same reference numerals, in particular for components using the same reference numerals, in principle, reference can also be made to other embodiments, in particular to the attached drawings. Figures 1 to 6 In order to distinguish these embodiments, the drawings and / or descriptions of the embodiments are shown in FIG. Figures 1 to 6 The reference symbols of the embodiments are followed by the letter a. Figure 7 In the embodiment of the invention, the letter a is replaced by the letter b.

[0101] Figure 7A drive device 10b of a drive unit (not shown here) for an electric bicycle (not shown here) is shown. 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 includes at least one mechanical control unit 22b. The control unit 22b has at least one friction unit 24b configured to generate an adjustment 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 includes at least one force transmission element 42b for transmitting the driving force of the drive unit. The spring unit 26b includes at least one spring element 32b, which is fixed to the assembly structure of the clamping element holding body 36b of the clamping element unit 18b, and the assembly structure extends into the through-portion 44b of the force transmission element 42b, in particular through the through-portion.

[0102] The clamping element unit 18b includes at least one pretensioning unit 112b configured to generate a pretensioning force. The pretensioning unit 112b includes at least one spring element 114b, 116b, which is configured as a leaf spring. The at least one leaf spring is preferably arranged on another assembly structure of the clamping element retaining body 36b, and the other assembly structure extends into another through-portion 44b' of the force transmission element 42b, in particular passes through the other through-portion. The leaf spring preferably includes a support body 120b and a spring leaf 122b. The support body 120b is preferably fixed to the other assembly structure. The support body 120b is preferably configured as a support body similar to the spring element 32b, in particular having a connecting element, such as in Figure 6 As shown in (see Figure 6 The spring leaf 120b preferably extends from the end facing away from the clamping element holding body 36b through the further through-portion 44b' in the direction of the clamping element holding body 36b. The bend of the spring leaf 120b is preferably configured to abut against a wall of the force transmission element 42b that delimits the further through-portion 44b' in at least one operating state of the drive device 10b.

[0103] The spring element of the friction unit 24b is preferably not arranged on the other mounting structure to which the leaf spring is fixed. The clamping element retaining body 36b preferably includes a plurality of, for example, four mounting structures here, which are respectively equipped with one of the spring elements 32b of the friction unit 24b or one of the leaf springs of the pretensioning unit 112b. As shown here by two samples in each case, the number of leaf springs and spring elements 32 of the friction unit 24b can be the same or different, for example in a ratio of 3:1 or 1:3. The distribution of the spring elements 32b and the leaf springs can be rotationally symmetrical about the rotation axis 34b of the drive device 10b, or irregular. In addition to the leaf springs, the pretensioning unit 112b can also have compression springs, which act on the mounting structure to which the spring element 32b of the friction unit 24b is fixed.

Claims

1. A drive device (10a; 10b) for a drive unit (12a; 12b) of an electric bicycle (14a; 14b), comprising a bidirectional freewheel (16a; 16b), wherein: The free wheel (16a; 16b) comprises at least one clamping element unit (18a; 18b), characterized in that the clamping element unit (18a; 18b) comprises at least one pretensioning unit (112a; 112b) which is configured to generate a pretensioning force.

2. The drive device (10a; 10b) according to claim 1, characterized in that The clamping element unit (18a; 18b) comprises at least one mechanical control unit (22a; 22b), wherein the control unit (22a; 22b) comprises a friction unit (24a; 24b) configured to generate an adjustment force, and the control unit (22a; 22b) comprises the at least one pretensioning unit (112a; 112b).

3. The drive device (10a; 10b) according to claim 2, characterized in that The friction unit (24a; 24b) and the preload unit (112a; 112b) are arranged such that the adjustment direction of the friction unit (24a; 24b) and the direction of action of the preload force are preferably oriented crosswise to one another, in particular at least substantially perpendicularly.

4. The drive device (10a; 10b) according to one of the preceding claims, characterized in that The pretensioning unit (112a; 112b) has at least one spring element (114a, 116a; 114b, 116b).

5. The drive device (10a) according to claim 4, characterized in that The at least one spring element (114a, 116a) is designed as a compression spring.

6. The drive device (10b) according to claim 4 or 5, characterized in that: The at least one spring element (114b, 116b) or a further spring element of the pretensioning unit (112b) is designed as a leaf spring.

7. The drive device (10a) according to any one of claims 2 to 6, characterized in that The pretensioning unit (112a) and the friction unit (24a) are arranged on a same receiving area (92a) of a clamping element holding body (36a) of the control unit (22a).

8. The drive device (10b) according to any one of claims 2 to 6, characterized in that The pretensioning unit (112b) and the friction unit (24b) are arranged on different receiving areas (92b) of a clamping element holding body (36b) of the control unit (22b).

9. A drive unit (12a; 12b) for an electric bicycle (14a; 14b) having a drive device (10a; 10b) according to one of the preceding claims.

10. An electric bicycle (14a; 14b) having a drive unit (12a; 12b) according to claim 9.

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