Device for transmitting effective drive torque from reciprocating motion to circular motion

Abstract

A mechanical system converts a reciprocating motion of a crank into a circular motion by using the crank or a lever, thereby converting a force applied by a user into a drive torque applied on a drive shaft. The mechanical system of the invention makes it possible to generate an effective torque on the crank used by a force simultaneously applied to the crank or alternately applied to the crank, wherein the applied force may be a pulling force or a pushing force.

Description

Background Art

[0001] Known conventional mechanical systems with cranks or levers are used to convert the energy provided by the user into mechanical energy, which can be used, for example, to provide a torque suitable for rotating a drive shaft. In these cases, the driving torque is generated by the user through the crank with a thrust or pull force.

[0002] The length of the crank is generally determined by the width and flexibility of the limb used to apply the force, or the field of use (eg, racing bike, mountain bike, fitness bike, touring bike, hand bike, etc.).

[0003] In traditional crank systems with circular motion, it is felt necessary to limit the length of the crank because excessive crank length will not allow the user to perform an efficient biomechanical movement.

[0004] In fact, excessive crank length can lead to incorrect posture or cause illness due to incorrect limb movement.

[0005] Conversely, short crank lengths produce overall inefficient biomechanics.

[0006] When the crank is at dead center, the muscle force applied by the user produces a torque with a net force of zero.

[0007] In fact, in a traditional bicycle with a circular crank movement, it is objectively difficult to exert force when passing the dead points (bottom dead center and top dead center) when it is necessary to produce high torque at low rotation speeds.

[0008] Furthermore, in conventional systems with circular motion, the cranks are timed at 180° or in parallel (for example, in the case of a hand-operated bicycle), transmitting force with a fixed period (180°+180°).

[0009] The most direct way to reduce the above problems is to limit the length of the crank.

[0010] Thus, shorter crank lengths allow for increased pedaling cadence, often used to improve biomechanical performance.

[0011] This system is effective and generally easy to implement, but it reduces the maximum applicable torque because the length of the crank itself is directly proportional to the drive torque produced.

[0012] Some methods in the prior art are described below, which are aimed at improving the biomechanical performance of the user's energy-driven mechanism.

[0013] A bicycle is a vehicle propelled by the muscle power of the user's limbs. It usually consists of a frame to which two aligned wheels are attached and equipped with a mechanical system for transmitting power to the drive wheels.

[0014] TO2010A000499 discloses a device in which a circularly moving crank can transmit effective torque in both directions of crank rotation (clockwise and counterclockwise) to a drive shaft via a unidirectional flywheel.

[0015] Two flywheels are mounted on the drive shaft, with the inner diameter of the flywheel meshing directly with the shaft and the outer diameter meshing with the two bevel gears.

[0016] The two bevel gears are connected to each other via a pinion to reverse the direction of rotation.

[0017] There are some disadvantages to pedal direction reversing devices of the type described above.

[0018] In particular, the device provides a circular motion of the crank, which does not allow the installation of cranks longer than conventional lengths. In addition, the cranks, which are timed at 180°, maintain an effective dead-center limit.

[0019] US 2013 / 0205928 discloses a transmission device for a device having a crank or a lever, wherein the crank itself performs a reciprocating motion.

[0020] The two cranks are connected to the drive shaft via a flywheel.

[0021] The two cranks are reciprocated in a reciprocating motion by a mechanical rotation inverter consisting of a bevel gear and pinion gear system. The cranks are connected to a flywheel through gears, which is appropriately mounted on the drive shaft to transmit torque to the drive shaft in the desired direction. If desired, the non-pushing crank can also be used to generate input torque (through pulling force).

[0022] The device described in US2013 / 0205928 has some drawbacks, such as the inability to time the crank in any position relative to the position of the transmission member (e.g. chain, belt, cardan shaft). In fact, the crank is mounted on the same side as the driving crown wheel and must work in an arc that does not interfere with the transmission device necessary to transmit the movement to the vehicle drive wheels.

[0023] A device with a variation of the aforementioned system is known from EP 2 679 480 A. The device is made by disconnecting the two cranks from each other and pulling the cranks themselves back into the active position by means of springs.

[0024] The key point of this system lies mainly in the fact that it is not possible to transmit both pushing and pulling forces at the same time, since one of the stages is achieved by a spring that can only pull the lever back to the pushing position.

[0025] In view of the above prior art, it remains desirable to provide a system that is capable of transmitting effective torque to a drive shaft through a crank or lever, thereby overcoming the problems associated with crank position and crank length.

[0026] It is also desirable that the system be energy efficient by being able to provide improved biomechanical properties. Summary of the invention

[0027] The present invention relates to an alternative lever transmission device, particularly but not exclusively for use in pedal-powered vehicles. A lever made of a crank is selectively connected to a drive shaft by a one-way coupling (flywheel or overdrive coupling). A reversing mechanism allows the flywheel to be alternately engaged on the drive shaft so that the torque generated by the crank can be transmitted in the desired direction, such as push or pull torque.

[0028] In addition, the non-pushing cranks can also be used to apply pulling force. The user can reverse the stroke of the cranks at any time using only force applied by the feet, and the range of motion of the arc is infinitely variable.

[0029] The present invention relates to a mechanical transmission device that can convert the force applied by the user's limbs into an effective driving torque on a drive shaft through a crank or a lever. Through the action of a flywheel (a one-way mechanical system), the reciprocating crank transmits the torque to the drive shaft in the desired direction.

[0030] Furthermore, the mechanical device according to the invention allows generating torque values ​​on the drive shaft by applying pulling and pushing forces through the crank. The forces applied to the crank allow effective torque on the drive shaft over the entire range of use without having to make the crank itself travel a complete 360° circular trajectory.

[0031] The aforementioned mechanical device makes it possible to provide driving torque to the drive shaft even under minimal vibrations.

[0032] By limiting the movement of the crank to a circular arc, cranks with extreme lengths can be used, allowing higher torque values ​​than conventional circular motion mechanical systems.

[0033] In the proposed device, the crank moves in a reciprocating motion and transmits torque to the drive shaft, which results in a circular motion. The possibilities of motion are infinitely variable. The user can reverse the pedal stroke at any time using only the force applied to the crank. The device allows the crank to be timed on any desired arc.

[0034] The invention is applicable to any pedal powered vehicle, as well as to any other machine using a moving bar as power input, where the power of the user's limbs is used. The figures attached to this application show, by way of non-limiting example, the application of the invention to a bicycle frame.

[0035] In particular, the present invention provides a device capable of increasing the transmitted torque by increasing the length of the crank.

[0036] The mechanical device according to the invention also allows the torque generated by the crank to be transmitted through infinitesimal oscillations.

[0037] Furthermore, the invention relates to a mechanical device in which the thrust applied by the user is independent of the length of the crank, so that for the same force a greater torque can be generated even if the vibrations of the lever or crank itself are reduced.

[0038] Another particular aspect of the present invention is the ability to time the cranks so that they are parallel to each other, by virtue of the preferred embodiments of the present invention.

[0039] The aforementioned solution allows to apply the thrust generated on both cranks simultaneously and then to reverse the traction force at the end of the desired oscillation.

[0040] This embodiment is particularly useful when the force applied by the user is generated by the upper extremities of the body. This system allows for more linear body and arm movements than conventional circular systems.

[0041] Preferred embodiments of the device according to the invention are obviously used in conjunction with bicycles and pedal-powered vehicles.

[0042] In this and other embodiments, the user can position the cranks and select their timing to allow for biomechanically efficient use.

[0043] The flexibility of the crank timing makes it possible to vary the applied force and thus the overall center of gravity created by the weight of the user and the weight of the mechanism, in contrast to a conventional bicycle where the center of gravity cannot be changed because the direction of the thrust cannot be changed (the direction of the driving torque).

[0044] The fact that the invention allows the cranks to be timed to a desired position has many advantages, for example in the case of applications on mountain bikes (MTBs) where more grip on the drive wheel is required due to the constantly changing terrain of the route and sometimes unstable grip. The cranks can be appropriately timed to provide thrust closer to the rear wheel (e.g. Fig.10 The posture adopted by the user in this configuration allows for more efficient thrusting, with obvious benefits not only to thrusting but also to the user's balance.

[0045] If the forces exerted by the lower limbs are used, the mechanical device of the invention allows the user to work with the legs in parallel to facilitate the posture, thus ensuring greater safety and stability in controlling the vehicle and greater and more natural flexibility of the legs compared to traditional systems in which the cranks are timed at 180 degrees to each other.

[0046] In order to position the cranks backwards (opposite to the direction of movement) so that one of the cranks would interfere with the torque transmission system (chain, etc.), the invention achieves this by means of a special lever (torque transmitter) which bypasses the crown gear and eliminates the interference, e.g. Figure 1 Shown is a conventional crank (left) and torque transmitter (right). The present invention also allows for minimal torque to be applied with minimal crank swing.

[0047] Therefore, the device is particularly suitable when the user has incomplete mobility of the limbs, and it is useful to have a device that allows the desired function to be obtained according to the needs of the user to reduce the arc of use.

[0048] The width is independently adjusted by the user and the device adapts to the desired thrust arc, allowing thrust to be transferred from one crank to the other at any time with the same transmission ratio.

[0049] A variation of the device according to this description allows the rotation of the drive shaft and the driven gear to be fixed, eliminating the flywheel usually mounted on the rear wheel of the bicycle. When the crank does not transmit torque, this configuration receives inertia from the flywheel or the driven gear so that the transmission member can remain in motion. The aforementioned configuration is intended to make the rotation speed of the drive shaft more stable and uniform, and thus improve the performance constant generated by the force applied by the user.

[0050] Furthermore, the aforementioned configuration allows the chain to be in constant motion even at low speeds, so a vehicle equipped with a gearbox will be able to change gear ratios without having to move the cranks.

[0051] Finally, the drive shaft associated with the drive crown gear is not connected directly to the crank, but can be connected to the electric motor through an appropriate transmission system, allowing power-assisted pedaling.

[0052] Additional features and advantages of the invention are described and will become apparent from the detailed description of the invention and can be inferred from the dependent claims.

[0053] In order to meet possible needs, those skilled in the art may change and modify the embodiments of the above-described mechanical system, or may replace these elements with other functionally equivalent elements without departing from the scope of the appended claims. Each feature described above belonging to the possible embodiments can be implemented independently of the other embodiments described. BRIEF DESCRIPTION OF THE DRAWINGS

[0054] Additional features and advantages of the present invention are described and will become apparent from the detailed description of the invention and the following drawings, in which:

[0055] Figure 1A functional diagram showing a preferred embodiment of a device according to the invention comprising a drive torque transmitter associated with an offset crank;

[0056] Figure 2 A functional diagram showing a preferred embodiment of a device according to the invention comprising a drive torque transmitter associated with a parallel crank;

[0057] Figure 3 A functional diagram showing a preferred embodiment of a device according to the invention comprising a drive torque transmitter associated with an offset crank and a generator mounted on a driven gear;

[0058] Figure 4 shows a functional diagram of a preferred embodiment of a device according to the invention comprising a drive torque transmitter associated with an offset crank and a generator connected to a drive shaft;

[0059] Figure 5 shows a functional diagram of a preferred embodiment of a device according to the invention comprising a drive torque transmitter associated with a parallel crank and a generator mounted on a driven gear;

[0060] Figure 6 shows a functional diagram of a preferred embodiment of a device according to the invention comprising a drive torque transmitter associated with a parallel crank and a generator connected to a drive shaft;

[0061] Figure 7 An axonometric view showing a preferred embodiment of the device according to the invention;

[0062] Figure 8 An axonometric view showing a preferred embodiment of the apparatus according to the invention using a double spur gear transmission, wherein the main components are highlighted;

[0063] Fig. 9 shows an axonometric view of a preferred embodiment of an apparatus according to the invention using a gear transmission and a chain / belt transmission, with the main components highlighted;

[0064] Fig.10 An example of mounting a preferred embodiment of the device according to the invention on a bicycle frame is shown;

[0065] Fig.11 Another example of application of a preferred embodiment of the device according to the invention is shown;

[0066] Fig.12 shows an axonometric view of a preferred embodiment of the device according to the invention, which is equipped with a double transmission chain, one of which allows a reversal of the direction of rotation;

[0067] Fig.13 Shows Fig.12 Functional diagram of an embodiment of the present invention, the embodiment comprising a drive torque transmitter associated with an offset crank;

[0068] Fig.14 A functional diagram showing a preferred embodiment of a device according to the invention comprising a drive torque transmitter associated with an offset crank, and

[0069] Fig.15 An axonometric view of a preferred embodiment of the device according to the invention is shown, with some components highlighted.

[0070] The following description of exemplary embodiments refers to the accompanying drawings. The same reference numerals in different drawings represent the same or similar elements. The following detailed description does not limit the invention. The scope of the invention is defined by the appended claims. DETAILED DESCRIPTION

[0071] The examples described below are preferred embodiments of the present invention. Other embodiments capable of reproducing the present invention are possible and are intended to be a part of the present invention. The present invention will be described primarily with reference to its use in conjunction with a bicycle, it being understood that such a combination is merely illustrative and does not limit the scope of the present invention, and the present invention is also applicable to other fields where it is necessary to utilize circular motion, which is generated by reciprocating a movable lever or crank by force applied by a user.

[0072] Thus, the present invention is directed to a device for transmitting a continuous drive torque from the actuation of a lever, wherein the lever does not rotate continuously, but rather travels in an arc both forward and rearward simultaneously or in a reciprocating manner.

[0073] Reference Figure 7 and Figure 8 , in a preferred embodiment, a device according to the invention is shown for mounting on a sled vehicle, such as a bicycle.

[0074] In this preferred embodiment, the device according to the invention comprises a support box 100, which in this case is suitable for being fixed to, for example, a bicycle frame and is rotatably connected to a central shaft 8, the ends of which are connected to the first crank 6 and the second crank 1 in a manner that will be explained later. Said support box 100 can generally also be integrated into the structure of the vehicle. Each crank preferably comprises a circular hub and an arm, which is used to fix it to the support box 100 in a rotatable manner, and the arm can include a connection point for the pedals 1A, 6A. In addition, the shaft 8 can be associated with at least one crown gear 9. Said at least one crown gear 9 is suitable for driving a chain, which connects, for example, the crank mechanism to a rear transmission pinion. All conventional mechanisms for connecting a chain from a crown gear to one or more transmission pinions can be used in combination with the device according to the invention.

[0075] However, the present invention can be used with many other types of mechanisms. Another example is a drive shaft that connects the crank device to the rear gear. Since these components are known to those skilled in the art, they will not be described in detail or described within the scope of this specification.

[0076] Typically, the user can provide the driving force by pushing with one foot, for example, a pedal attached to the end of the first crank 6. This will cause the first crank 6 to move counterclockwise (the crank can be facing in the direction opposite to the direction of movement). The reversing gear of the device according to the invention will cause the second crank 1 to move clockwise. Therefore, when the user pushes on the first pedal, the second pedal rises. Once the first pedal reaches the bottom of its stroke, the process is reversed; the second pedal will be in a raised position, ready to be pressed down by the user. At this point, the reversing gear of the device according to the invention will cause the movement of the first pedal to reverse, and the first pedal will rise to a position suitable for being pushed by the user, starting the cycle again.

[0077] For more details, refer to Figure 1 In the functional diagram in FIG. 1 , the support box 100 includes a drive shaft 8, the ends of which are connected to the first crank 6 and the second crank 1. The transmission between the two parallel shafts 8, 8a uses a pair or a set of three gears, chains or belts for direct and reverse transmission, and includes a one-way coupling - or flywheel - 7a, 7b, which is designed to ensure that the two cranks 1, 6 always rotate in opposite directions as a whole and alternately engage with the shaft 8 to transmit the torque applied to the cranks 1, 6 by the user.

[0078] The aforementioned flywheel or one-way coupling acts so that when the motor element rotates in one direction, the motor element pulls the driven element, and when the driven element rotates in the opposite direction, the motor element automatically separates from the driven element. The aforementioned flywheels are known to those skilled in the art and are commercially manufactured in various modes and forms; therefore, they will not be described in more detail during the course of this specification.

[0079] The first crank 6 is connected to the first transmission wheel 5. In order to bypass the transmission members 9, 10, the second crank 1 is connected to a lever acting as a torque transmitter 2, which is connected to the second transmission wheel 3. The first and second transmission wheels 5, 3 are placed next to each other, supported by the transmission shaft 8, and have competing axes.

[0080] In order to be able to reverse the direction of rotation of the above-mentioned first and second gears 5, 3, a third gear 4a is mounted on the auxiliary shaft 8a, connected to the second gear 3. The gear 4a is integral with a transmission wheel 4b, which is also keyed to the auxiliary shaft 8a. The transmission wheel 4b is connected to the transmission wheel 5 by a transmission element 60 (chain, belt, rope or double gear transmission). In short, the device provides two transmission devices to the auxiliary shaft 8a, one of which reverses the direction of rotation (between the transmission wheels 3, 4a) and the other (between the transmission wheels 4b, 5) maintains the direction of rotation. There may be a gear kinematic mechanism 4, which is able to mesh with the first gear 5 and the second gear 3. Preferably, the aforementioned first and second gears 5, 3 are characterized by a tooth profile height less than or equal to 12 mm. In a preferred embodiment of the present invention, the first and second gears 5, 3 and the third gear 4 may be conical. Alternatively, the first and second gears 5, 3 may be cylindrical, and the gear kinematic mechanism includes pinions 4a, 4b with parallel axes, such as Figure 8 In summary, the reverse motion between the transmission wheels 5 and 3 can be achieved by many different types of mechanisms, which are still within the scope of the present invention.

[0081] The first crank 6 and the second crank 1 are associated with a first one-way coupling 7a and a second one-way coupling 7b, respectively, which are suitable for transmitting the torque applied by the user to the cranks 1, 6 to the drive shaft 8 and moving the drive shaft 8 in a desired direction. The one-way couplings 7a, 7b are such that when the cranks are driven by the user in a predetermined direction (for example, counterclockwise), the cranks 1, 6 are locked with the shaft 8, and when the cranks are driven in the opposite direction (for example, clockwise) relative to the predetermined direction, the cranks 1, 6 are disengaged from the shaft 8.

[0082] Furthermore, the drive shaft 8 may be connected to a crown gear 9 which may transmit torque to a driven crown gear 11 via a suitable transmission member 10, which may be integrally connected to a driven gear 12. The transmission member 10 may be made, for example, of a transmission chain, as shown in the attached Fig.10 and 11 shown.

[0083] The above-mentioned lever 2 used as a torque transmitter makes it possible to integrate the second crank 1 onto the second gear 3 without interfering with the crown wheel 9 and the transmission member 10. This solves the problem of interference with the driving crown wheel 9 and the transmission member 10, which would occur, for example, if the crank 1 worked in an arc coinciding with the position of the transmission member 10.

[0084] Figure 2 Shows Figure 1 , wherein the support box 100 provides the first crank 6 and the second crank 1 rigidly connected to each other with parallel axes. The torque transmitter 2 rigidly connected to the cranks 1, 6 again allows torque to be transmitted without interfering with the rotation of the drive crown wheel 9. This parallel crank configuration allows thrust and pull forces to be generated on the drive shaft 8.

[0085] Figure 3 Shown with Figure 1 The configuration shown is compared to an alternative configuration in which the driven crown gear 11 is connected directly or through a gear to the generator / motor 30, which in turn is connected to the driven gear 12. When the cranks 1, 6 generate an effective torque on the drive shaft 8, the transmission member 10 transmits the torque to the crown gear 11, thereby allowing the resultant torque given by the torque generated by the cranks 1, 6 and the generator / motor 30 to be generated on the driven gear 12. When the cranks 1, 6 do not transmit an effective torque to the drive shaft 8, the generator / motor 30 receives the mechanical torque from the driven gear 12 by converting the mechanical torque into electrical energy.

[0086] Figure 4 Shown with Figure 1 The configuration shown is compared to an alternative configuration in which the drive shaft 8 is connected to the generator / motor 30 directly or through a gear through a transmission member 13. When the crank 1, 6 transmits active torque to the drive shaft 8, the generator / motor 30 provides auxiliary torque to the drive shaft 8 by working as a motor. In the stall phase of the crank 1, 6, the generator / motor 30 receives the mechanical torque generated by the inertia of the driven gear 12 through the transmission member 10 to generate current. The generator / motor 30 can also be advantageously placed inside the support box 100, or placed outside the vehicle structure by appropriate anchoring.

[0087] Figure 5 Shown with Figure 3 The configuration shown is compared to an alternative configuration in which the support box 100 requires the cranks 1, 6 to be rigidly connected to each other with parallel axes. Also in this case, the torque transmitter 2 rigidly connected to the cranks 1, 6 allows an advantageous torque transmission without interfering with the rotation of the drive crown wheel 9. This configuration with parallel levers or cranks allows the generation of thrust and pull forces on the drive shaft 8.

[0088] Figure 6 Shown with Figure 4 The configuration shown is compared to an alternative configuration in which the support box 100 requires the cranks 1, 6 to be rigidly connected to each other with parallel axes. Likewise, the torque transmitter 2 rigidly connected to the cranks 1, 6 allows torque to be transmitted without interfering with the rotation of the drive crown gear 9. Likewise, the configuration with parallel levers or cranks allows thrust and pull forces to be generated on the drive shaft 8.

[0089] Attached Figure 7 Shows the corresponding Figure 1 The embodiment of the functional diagram is shown, in which the cranks 1 , 6 are connected to the outside of the support box 100 .

[0090] exist Figure 8 , another embodiment of the reversal kinematic motion using only cylindrical gears is shown. In this preferred embodiment, the gear kinematic motion that allows the mechanical reversal of the first and second gears 5, 3 is achieved by using parallel axis pinions 4a, 4b. The force F1 applied to the second crank 1 integral with the torque transmitter 2 transmits the torque to the second gear 3. Therefore, the second gear 3 meshes with the first pinion 4a, which in turn meshes with the second gear 4b, which in turn allows it to mesh with the second gear 5. The second gear 5 integral with the first crank 6 transmits a torque opposite to the torque direction of the force F1 to the first one-way coupling 7a. The first one-way coupling 7a in turn sets the drive shaft 8 integral with the drive crown gear 9 into motion, allowing it to rotate in the desired direction shown by the arrow ω1.

[0091] The above-described torque transfer occurs in the same configuration when the force applied to the first crank 6 allows the drive shaft 8 to be pulled by the second flywheel 7b.

[0092] The aforementioned torque transmission is achieved by the forces F1 and F2, which pull the drive shaft 8 in the desired direction through the one-way couplings 7a, 7b. In other words, if a thrust from above is applied to one of the cranks, the transmission wheel adjacent to this crank will be set to rotate in the same direction as the movement of the crank being driven, while the other transmission wheel on the shaft 8 will rotate in the opposite direction. One of the two gears will still be meshed on the shaft 8 through its one-way coupling. In this way, the reciprocating motion imparted to the cranks 1, 6 through the one-way couplings 7a, 7b allows a continuous circular motion to be generated on the drive shaft 8.

[0093] Fig. 9 Shows Figure 8 A preferred alternative embodiment of the embodiment shown, wherein the first gear 3 meshes with the gear 4a. The gear 4a, which is integral with the gear 4b, transmits (or receives) motion to the gear 5 via the transmission element 60. The lever 2, which acts as a torque transmitter, is integral with the gear 3, bypassing the transmission members 9, 10 and making the gear integral with the crank 1. This configuration allows the crank 1 to work in an arc adjacent to the transmission members 9, 10.

[0094] Fig.12 Shows Figure 8 An additional preferred alternative embodiment of the illustrated embodiment, in which the first gear 5, the second gear 3 and the pinions 4a, 4b are replaced by crown gears 50 and 60 and crown gears 40a and 40b, respectively. In this embodiment, a transmission chain 80 connects the crown gear 50 with the crown gear 40B, thereby allowing the crown gear 40B to rotate in the same rotational direction, and a transmission chain 70 connects the crown gear 60 with the crown gear 40a, and the chain 70 is installed to allow the crown gear 60 to rotate in the opposite direction relative to the crown gear 40a.

[0095] By reversing the direction of rotation, the torque transmitted on the crown gear 60 is transmitted to the crown gear 40a. Said crown gear 40a, integrated on the same rotation axis, transmits the torque to the crown gear 40b, which in turn transmits the torque to the crown gear 50. Fig.12 The preferred embodiment can also be achieved by reversing the connection of the chains 80 and 70 , while ultimately maintaining the opposite direction of rotation between the crown gear 60 and the crown gear 50 .

[0096] Fig.13 Shown according to Fig.12 Functional diagram of the device shown.

[0097] exist Fig.10 In, according to Figure 7The illustrated version of the device of this description is mounted on a bicycle frame 40 on which the crown gear 9 allows a driven crown gear 11 - or a set of driven crown gears - to rotate a driven gear 12 via a transmission chain 10. The driven gear 12, which is integral with the driven crown gear 11, allows the moment of inertia to be transmitted to the driving crown gear 9 when the cranks 1, 6 do not transmit torque to the drive shaft 8 via the one-way couplings 7a, 7b.

[0098] Fig.11 Shown in Figure 3 An example of application of the configuration described in the diagram of . The device according to the invention transmits torque from the driving crown gear 9 to the driven gear 11 or driven gear set via the transmission chain 10. The driven gear 11, which is integral with the generator / motor 30, allows the resultant torque given by the mechanical torque generated by the device and the torque provided by the generator / motor 30 to be transmitted to the driven gear 12. When the device does not transmit active torque to the driven gear 11, the inertia of the movement of the gear 12 allows the generator / motor 30 to generate current.

[0099] The device according to the present description makes it possible to solve the problems of the prior art described above and to be advantageously applied in pedal-powered vehicles (bicycles, racing bikes, mountain bikes (MTB), fitness bikes, touring bikes, hand bikes, etc.) and in devices used, for example, in gymnasiums, for arm and leg training, due to the flexibility of use and configuration.

Claims

1. A device for transmitting driving torque, comprising: Axis (8); a crown gear (9), the crown gear (9) being associated with the shaft (8); a first crank (6) connected to a first transmission element (5, 50); a second crank (1), said second crank (1) being connected to a second transmission element (3, 60); a first one-way coupler (7a), the first one-way coupler (7a) being connected to the first crank (6); a second one-way coupling (7b) connected to the second crank (1), the one-way coupling (7a, 7b) being adapted to lock the crank (1, 6) with the shaft (8) when the crank is actuated by a user in a predetermined direction, and to disengage the crank (1, 6) from the shaft (8) when the crank is actuated in an opposite direction relative to the predetermined direction; a torque transmitter (2) connecting the second crank (1) to the second transmission element (3, 60), the torque transmitter (2) being adapted to bypass the crown gear (9) to avoid interfering with the movement of the crown gear (9) during the movement of the crank (1, 6); a reversing element, the reversing element comprising a kinematic mechanism adapted to engage with the first transmission element (5, 50) and the second transmission element (3, 60) and adapted to force the cranks (1, 6) to rotate in opposite directions, Characterized in that the kinematic movement is of the parallel-axis type and is suitable for providing a continuous driving torque to the shaft (8) and the crown wheel (9) during the movement of the cranks (1, 6).

2. The device according to claim 1, characterized in that It comprises a supporting box (100).

3. Device according to one or more of the preceding claims, characterized in that The one-way couplers (7a, 7b) are adapted to engage in one direction and release movement in the opposite direction.

4. Device according to one or more of the preceding claims, characterized in that The one-way coupler (7a, 7b) is accommodated in the supporting box (100).

5. Device according to one or more of claims 1 to 4, characterized in that The one-way coupler (7a, 7b) is directly mounted on the crank (1, 6).

6. Device according to one or more of the preceding claims, characterized in that The support box (100) is integrated into the structure of the vehicle.

7. Device according to one or more of claims 2 to 6, characterized in that The crank (1, 6) comprises a hub, which is suitable for fixing the crank (1, 6) to the support box (100) in a rotatable manner.

8. Device according to one or more of the preceding claims, characterized in that The crank (1, 6) comprises an arm provided with fixing means for a pedal (1A, 6A).

9. Device according to one or more of the preceding claims, characterized in that The crown gear (9) is associated with a transmission member (10) adapted to transmit the movement of the crown gear (9) to a driven crown gear (11).

10. The device according to the preceding claim, characterized in that The crown gear (11) is connected to a generator / motor (30).

11. Device according to one or more of the preceding claims, characterized in that The drive shaft (8) is connected to a generator / motor (30) via a transmission member (13).

12. Device according to one or more of the preceding claims, characterized in that The first crank (6) and the second crank (1) are rigidly connected to each other so that their axes are parallel.

13. Device according to one or more of the preceding claims, characterized in that The first transmission element is connected to the crank (6) and comprises a first crown gear (5), the second transmission element is connected to the crank (1) and comprises a second crown gear (3), the first crown gear (5) and the second crown gear (3) being coaxial with the output shaft (8).

14. Device according to the preceding claim, characterized in that The reversing element comprises a gear kinematics mechanism (3, 4a) and a transmission element (60) acting on two transmission wheels (4b, 5).

15. Device according to the preceding claim, characterized in that The gear kinematic mechanism comprises two gears (5, 3) and two pinions (4a, 4b).

16. Device according to one or more of claims 13 to 15, characterized in that The tooth profile height of the gears (3, 5) is less than or equal to 12 mm.

17. Device according to one or more of claims 1 to 12, characterized in that The first transmission element comprises a first crown gear (50) and the second transmission element comprises a second crown gear (60), the first crown gear (50) and the second crown gear (60) being coaxial with the output shaft (8).

18. Device according to the preceding claim, characterized in that The reversing element comprises a crown wheel kinematic mechanism.

19. Device according to the preceding claim, characterized in that The crown gear and parallel axis kinematic mechanism comprises two crown gears (40a, 40b) and two transmission chains (70, 80) adapted to mesh the first crown gear (50) and the second crown gear (60) with the crown gears of the crown gear kinematic mechanism.

20. A pedal-powered vehicle comprising a device for transmitting drive torque according to one or more of the preceding claims.

21. Machine for training the arms and legs of a user, comprising a device for transmitting a driving torque or a drag torque according to one or more of the preceding claims.

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