Gearbox with energy storage

Abstract

The invention relates to a transmission (1) for generating a high-speed rotary motion from a low-speed rotary motion, comprising: - a drive shaft (20) that rotates at low speed; - a drive wheel that sits on the drive shaft; - an output shaft (40) that rotates at high speed; - a driven element that engages with the drive wheel, wherein the engagement comprises a first phase in which the drive wheel drives the driven element and a second phase in which the drive wheel and the driven element are decoupled from each other; - an energy storage device (70) which absorbs energy in the first phase of the engagement by moving the output element and releases the absorbed energy via the output element to rotate the output shaft in a second phase of the engagement.

Description

[0001] The invention relates to a transmission for generating a high-speed rotary movement from a low-speed rotary movement.

[0002] Such a transmission is well known in the art. The transmission comprises a drive shaft and a drive gear mounted on the drive shaft. The drive shaft rotates at a comparatively low speed, as is the case, for example, with a wind turbine with a slowly rotating rotor.

[0003] It is also known that the drive wheel in the form of a drive gear is in meshing engagement with an output element in the form of an output gear, which is mounted on an output shaft. By selecting the diameter or the number of teeth of the two gears, a gear ratio i of the transmission can be set. The gear ratio i corresponds to the ratio of the diameter of the output gear to the diameter of the drive gear (i = d Abtrieb / d Antrieb ). By selecting a large diameter for the drive gear paired with a small diameter for the output gear, very high speeds of the output shaft can be achieved, even if the drive shaft rotates only slowly. However, only a low torque is available at the fast-rotating output shaft. Transmission losses can also be high if a particularly low gear ratio (i << 1 or speed n Antrieb<< Speed ​​n Abtrieb ) is required.

[0004] The invention is therefore based on the object of providing an efficient transmission which, with a slowly rotating input shaft, enables a high speed of the output shaft and, at the same time, high torques at the output shaft.

[0005] The object underlying the invention is achieved with the combination of features according to claim 1. Embodiments of the invention can be found in the subclaims to claim 1.

[0006] According to the invention, the engagement comprises a first phase and a second phase, wherein in the first phase, the drive gear drives the output element, and in a second phase, the drive gear and the output element are decoupled from each other. The transmission comprises an energy storage device that absorbs energy during the first phase of the engagement by moving the output element and, in a second phase of the engagement, releases the absorbed energy via the output element to rotate the output shaft.

[0007] The energy absorbed by the energy storage device can be released abruptly, resulting in high torques and high speeds at the output shaft for a short time. This makes it possible, for example, to further accelerate an already rapidly rotating flywheel using the output shaft.

[0008] In the second phase, the drive gear and the output element are decoupled from each other. Decoupling here means that the output element can move freely and at any speed to drive the output shaft, without the drive gear constituting an obstacle to the output shaft.

[0009] The first phase and the second phase form a cycle that continuously repeats during operation of the transmission. Preferably, the duration of the second phase is significantly shorter than the duration of the first phase. In one embodiment, the transmission is designed such that the ratio of the duration of the first phase to the duration of the second phase is at least 3, 4, or 6. In addition to the first phase and the second phase, the cycle can include further phases, which will be discussed later.

[0010] The energy storage device can have a coil spring that is tensioned in the first phase of engagement. In the second phase, the coil spring relaxes and releases energy in a relatively short time, which is used to drive the output shaft. Alternatively or additionally, the energy storage device can have a cylinder with a piston and a displacement volume containing a gaseous fluid. In the first phase, the piston is moved in the cylinder so that the displacement is reduced and the gaseous fluid is compressed. In the second phase, the pressure in the displacement volume is used to move the piston with relatively high speed and force to drive the output shaft.

[0011] A first freewheel can be provided between the output element and the output shaft, allowing the output element to drive the output shaft but not decelerate or block it. The first freewheel can be designed so that during the first phase, in which the energy storage device is being recharged, no torque or power is transmitted from the output element to the output shaft. During the second phase, the first freewheel ensures torque or power transmission from the output element to the output shaft.

[0012] In one embodiment, a second freewheel is provided so that the drive shaft does not brake the output element in the second phase. The second freewheel ensures that torque or power transmission between the output element and the drive wheel only takes place in the first phase.

[0013] The drive wheel can be designed as a drive gear. The drive gear can have a first angular range with teeth and a second angular range without teeth. In one embodiment, the first angular range is less than 180°, while the second angular range covers the remaining 360° of the drive gear.

[0014] The output element can be designed as an output gear. The output gear is in meshing engagement with the drive gear, at least during the first phase of engagement. If, for example, the first angular range of the drive gear extends over 90° and the output gear is a spur gear with teeth over the entire circumference, the first phase of engagement extends over only a quarter of the drive gear's full rotation. At three-quarters of the drive gear's full rotation, no torque is transferred from the drive gear to the output gear, since the drive gear lacks the teeth necessary for torque transfer in this angular range. The second phase of engagement, in which the energy storage device is discharged, preferably occurs during this time, when there is no meshing engagement between the drive gear and the output gear.The second phase can be shorter than the time of non-existent meshing engagement between the drive gear and the driven gear.

[0015] In one embodiment, the output element is designed as an output rack. In the first phase of engagement between the drive gear and the output rack, rotation of the drive gear leads to a preferably linear movement of the output rack. The linear movement of the output rack can, for example, tension a coil spring of the energy storage device.

[0016] At least one edge tooth of the first angular range of the drive gear can be replaceable. The edge tooth is a tooth of the toothing of the first angular range that directly borders the second angular range without teeth. Due to its edge position, the edge tooth must absorb particularly high forces in the first phase of engagement, since a force distribution across multiple teeth, as occurs in a middle range of the first angular range, is not possible. The edge tooth is preferably made of a hardened material. In addition, another edge tooth of the first angular range, now located at the end of the first angular range, can also be replaceable.

[0017] An edge tooth or an outer tooth of the drive rack can also be replaceable and / or made of hardened material. Here, too, the idea is to be able to replace the tooth or teeth of the gearing that are subject to particular stresses during transmission operation, or to make them particularly durable.

[0018] The intervention can also include a holding phase provided between the first and second phases, wherein the release of the energy stored in the energy storage device is blocked during the holding phase. This means that after the end of the first phase, the energy in the energy storage device is not used directly to drive the output shaft, but rather remains in the energy storage device for the duration of the holding phase and is only released after a time delay after the end of the first phase.

[0019] The transmission can include a blocking device that, in a blocking position, blocks the release of the energy absorbed by the energy storage device. The blocking device thus represents a possibility for implementing the holding phase in which the energy storage device is charged but not yet discharged.

[0020] The blocking position can be released by a release device. The release device can comprise a magnet or a controllable actuator that switches after a certain time, thus releasing the blocking position. Once the blocking position is released, the energy storage device can be discharged to drive the output shaft.

[0021] The blocking device can comprise two rods connected by a joint, which in a blocking position preferably lie essentially in a straight line. In the blocking position, the two rods form a buckling bar, which prevents movement of the output element only when the two rods lie in a straight line. The triggering device can be designed to exert a small lateral force on the joint upon triggering, which deflects the joint. The two rods then bend laterally and no longer offer any resistance to the movement of the output element.

[0022] At least one additional drive gear can be mounted on the drive shaft, which meshes with another output element. Preferably, three, four, five, or more than five drive gears are used to even out the drive of the output shaft. For this purpose, the first phase of engagement between the drive gear and the output element and a first phase of engagement between the additional drive gear and the additional output element are preferably phase-shifted. For example, with a total of four drive gears, the phase shift is preferably 90°.

[0023] The energy storage device can be assigned an adjustment mechanism that can be used to adjust the resistance force to be overcome when filling the energy storage device. A linear generator can also be provided, which converts a linear movement generated by the movement of the output element into electrical energy.

[0024] The invention is explained in more detail with reference to the exemplary embodiments illustrated in the drawings. They show: Fig. 1 shows a transmission according to the invention with an energy storage device; Fig. 2 a transmission according to the invention with several drive wheels; Fig. 3 a transmission according to the invention with a linear generator; Fig. 4 a transmission according to the invention with a blocking device; Fig. 5 the transmission of the Fig. 4 from the top; Fig. 6 further embodiments of the invention; and Fig. 7 different force paths acting on the energy storage device.

[0025] Fig. Figure 1 shows a transmission, designated in its entirety by 1. The transmission 1 comprises a drive wheel in the form of a drive gear 10, which is mounted on a drive shaft 20. The drive gear 10 has a toothing 11 that extends over a first angular range of the circumference of the drive gear 10. The first angular range covers approximately one-quarter, or 90°, of the circumference. A second angular range without toothing extends over approximately three-quarters of the circumference of the drive gear 10.

[0026] The transmission 1 further comprises an output element in the form of an output gear 30 with a toothing 31 extending over the entire circumference of the output gear 30. The wear gear 30 is mounted on an output shaft 40. A freewheel 50, also referred to here as the first freewheel, is provided between the output shaft 40 and the output gear 30. Its function will be described further below.

[0027] In addition, the transmission 1 comprises a linkage 60 and an energy storage device 70. The linkage 60 has a lever 61, a joint 62 and a piston rod 63. The lever 61 and the piston rod 63 are connected to one another in an articulated manner via the joint 62. The lever 61 is connected in a rotationally fixed manner to the output gear 30. If the drive gear rotates clockwise (see arrow 32), the lever 61 and thus, via the joint 62, the piston rod 63 in the illustration of the Fig. 1 moves upwards (see arrow 64).

[0028] The energy storage device 70 has a cylinder 71 and a piston 72, which is mounted for displacement along the longitudinal axis of the cylinder 71. The cylinder 71 is rotatably fixed on an axis 73, so that the cylinder can perform a pivoting movement about the axis 73 so that the linkage 60 is not blocked when the output gear 30 rotates. The piston 72 is connected to the piston rod 63 and, together with the cylinder 71, defines a displacement chamber 74 in which compressed air 75 is located. Via a line 76, which is connected to the displacement chamber 74, air can be supplied to or removed from the displacement chamber 74 in a controlled manner via a valve 77. The valve 77 can therefore be used to adjust the force that must be overcome to charge the energy storage device and that acts on the piston rod 63 when discharging the energy storage device. A chamber 78 below the displacement chamber 74 is connected to the environment. There is corresponding ambient pressure there.

[0029] The drive gear 10 is in engagement with the driven gear 30. The engagement has a first phase in which the drive gear 10 drives the driven gear 30. In the embodiment of the Fig. 1, the first phase is characterized by the meshing engagement between the toothing 11 of the drive gear 10 and the toothing 31 of the driven gear 30. During this meshing engagement, a counterclockwise rotation of the drive gear 10 (see arrow 12) leads to a clockwise rotation of the driven gear 30 (see arrow 32). Fig. 1 shows the gears 10, 30 in an angular position at the end of the first phase. Further rotation of the drive gear 10 results in the meshing engagement between the drive gear 10 and the driven gear 30 no longer being present. The first phase of engagement is thus followed by a second phase of engagement in which the driven gear 30 is no longer driven by the drive gear 10. Since the drive gear 30 can no longer be supported on the drive gear 10 in the second phase of engagement, the pressure acting on the piston 72 in the displacement chamber 74 causes the piston 72 and thus the piston rod 63 to be moved downward, i.e., opposite to arrow 64. The lever 61 is pivoted downward counterclockwise, thereby rotating the driven gear 30 counterclockwise. The freewheel 50 is designed so that the torque acting on the drive gear 30 is transmitted to the output shaft 40 in this direction of rotation.Due to the sudden release of pressure in displacement 74, the output shaft 40 experiences a strong rotational acceleration with a comparatively high torque. The second phase of the engagement thus represents the period during which the output shaft is driven by discharging the energy storage device.

[0030] For example, if the drive shaft 10 rotates at a speed of 15 rpm, a full rotation of the drive shaft 20 requires four seconds. Since the first angular range with the gearing 11 extends over a quarter of the circumference, the length of the first phase, in which the drive gear 10 drives the output gear 30, is one second. This means that one second is available for a complete stroke movement of the piston 72. The second phase of the engagement, in which the energy storage device 70 is discharged, is significantly shorter. In one embodiment, the second phase is at least a factor of 3 shorter than the first phase (for example, 250 ms).

[0031] If it is assumed that the drive shaft 20 rotates essentially at a constant speed (for example, at the above-mentioned 15 rpm), the second phase of the engagement is followed by a waiting phase in which there is no meshing engagement between the gears 10, 30. In this waiting phase, the drive gear 30 remains stationary until the toothing 11 of the drive gear 10 comes into contact with the toothing 31 of the driven gear 30 again. At an assumed speed of 15 rpm, the waiting time in the exemplary embodiment is Fig. 1 is slightly less than three seconds. The almost three seconds result from the difference between the time for one full rotation of the drive gear 10 minus the duration of the first phase minus the duration of the second phase (4 s - 1 s - 250 ms). The first phase, the second phase, and the waiting phase form a cycle, which is followed by further cycles in the case of a continuously rotating drive shaft.

[0032] The freewheel 50 allows the output shaft 40 to continue rotating counterclockwise when the output gear 30 is stationary during the waiting phase. During the waiting phase, no torque is transmitted between the output gear 30 and the output shaft 40. Only when the angular velocity of the output gear 30 is greater than the angular velocity of the output shaft 40 in the second phase of a subsequent cycle does the freewheel 50 ensure the torque transmission required to drive the output shaft 30. Since the output gear 30 rotates faster than the output shaft 30 in the second phase, it is possible to further accelerate the output shaft 30.

[0033] Fig. Figure 1 shows two black-backed teeth 13, 33, which are subject to particularly high stress due to their position in the toothing 11 and 13, respectively. These teeth 13, 33 may be interchangeable and / or specially hardened.

[0034] Fig. 2 shows a further embodiment, wherein the drive shaft 20 and the output shaft 40 are shown in a top view. In addition to the drive gear 10 already described above, further drive gears 10a are located on the drive shaft 20. On the output shaft 40, in addition to the output gear 30, further output gears 30a are arranged. The interaction of drive gear 10a and output gear 30a corresponds to the interaction of drive gear 10 and output gear 30 described above. Accordingly, each pair of drive gear 10a and output gear 30a can be assigned a linkage 60a and a freewheel 50a. The first phase of the engagement between drive gear 10 and output gear 30 is phase-shifted from a first phase of the engagement between output gear 10a and output gear 30a. For the five drive gears 30, 30a, the phase shift between the individual first phases is preferably 72° (360° / 5).This phase shift ensures a more constant rotation of the input shaft 20 and output shaft 40. The phase shift prevents the input shaft 20 from temporarily rotating without load, since there is always a gear pair (input gear / output gear) that is in the first phase.

[0035] As explained above, in the example of the Fig. 2 the output gears 30, 30a on the output shaft 40, wherein in the second phase the corresponding output gear 30 rotates at the same speed as the output shaft 40. However, it is also possible that between the output gears 30, 30a a gear ratio designed differently for each output gear is provided, so that the ratio of the speed of the output gear to the speed of the output shaft in the respective second phase is different for the individual output gears.

[0036] Fig. 3 shows a further embodiment of the transmission according to the invention. Components or details that are related to components or details of the embodiment of the Fig. 1 are similar or identical, are given the same reference numerals. This also applies to all other figures. In the following description of the figures, particular attention is drawn to the differences from the embodiment of Fig. 1 received.

[0037] The connection between the output gear 30 and the energy storage device 70 is made here via a crank drive 90 with a crank 91, a first connecting rod 92, and a second connecting rod 93. The crank 91 and the first connecting rod 92 are connected to one another via a joint 94. A further joint 95 ensures an articulated connection between the first connecting rod 91 and the second connecting rod 93. The energy storage device 70 here has a helical spring 79 which is connected to one end of the second connecting rod 93. By rotating the output gear 30, the crank mechanism 90 is actuated, whereby the second connecting rod 93 is moved up or down parallel to the longitudinal axis (see arrow 80) of the helical spring 79. In the first phase of the engagement between the drive gear 10 and the output gear 30, the helical spring 79 is tensioned, and the energy storage device 70 absorbs energy.In the second phase of engagement, this energy is released again to drive the output shaft 40 via the output gear 30. The preload of the spring 79 can be adjusted via an adjusting mechanism 81. The adjusting mechanism 81 has the same function as the valve 77 in the embodiment of FIG. Fig. 1. The adjusting mechanism 81 can be used to adjust the force that must be overcome to charge the energy storage device 70 or that is available when discharging the energy storage device 70.

[0038] The output shaft 40 can be connected to a generator for generating electricity. Additionally or alternatively, a linear generator 100 is provided, which can generate electricity when the second connecting rod 93 is displaced within the linear generator 100 along the arrow 80.

[0039] Instead of the linear generator 100, or in addition to it, a piston-cylinder unit with a displacement that suddenly increases its volume in the second phase can be provided. The displacement can be connected to a line through which a gaseous fluid flows, which cools due to the sudden increase in volume. If the fluid is a liquid, it can evaporate due to the sudden increase in volume and thus extract heat from the environment of the piston-cylinder unit. The piston-cylinder unit can thus be operated as a refrigeration machine.

[0040] The Fig. 4 and Fig. 5 show a further embodiment of the invention. Fig. 4 shows the gearbox 1 from the side, Fig. 5 the gearbox from above. The output element is designed as an output rack 110. The Fig. 4A and Fig. 4B show the drive rod 110 in different axial positions.

[0041] The drive rack 110 is similar to the second connecting rod 93 of the embodiment of the Fig. 3 is coupled to the energy storage device 70 and the linear generator 100. An axial displacement of the output rack 110 thus leads to a charging or discharging of the energy storage device 70. Electricity can also be generated in the linear generator 100 through the axial displacement.

[0042] Fig. Figure 4A shows the engagement between the drive gear 10 and the output rack 110 at the beginning of the first phase. The drive gear 10 rotates counterclockwise (see arrow 12) and is already in meshing engagement with one tooth of the gearing 11 of the output rack 110. Due to the rotational movement of the drive gear 10, the output rack 110 is rotated in the illustration of the Fig. 4 moves to the right and charges the energy storage device 70 (for example, by tensioning a coil spring). At an end 111 facing away from the energy storage device 70, the output rack 110 is connected to a blocking device 120.

[0043] The blocking device 120 has a first rod 121 and a second rod 122, which are connected to each other via a joint 123. An end of the first rod 121 facing away from the joint 123 is supported on a stationary pivot bearing 124. An end of the second rod 122 facing away from the joint 123 is pivotally connected to the wear rack 110 via a further joint 124. The displacement of the output rack 110 to the right (see arrow 126) causes the included angle between the first rod 121 and the second rod 122 to increase and ultimately amounts to 180° (see Fig. 5B). Fig. The position shown in Figure 5B can also be referred to as the end position, since further displacement of the output rack 110 in direction 126 is not possible. In the end position shown, the rods 121, 122 lie in a straight line. As long as the rods 121, 122 are not deflected from this end position, they block the output rack 110 from recoiling and thus the discharging of the energy storage device 70. The end position shown here can therefore also be referred to as the blocking position.

[0044] To stabilize the blocking position, the blocking device 120 has a magnet 127 that interacts with a magnet 131 of a triggering device 130. The magnets 127, 131 ensure that the blocking position does not collapse accidentally and the energy storage device 70 is not accidentally discharged. The triggering device 130 has a trigger rod 132 that interacts with a rotatable cam 133. By rotating the cam 133, the trigger rod 132 can be axially displaced. In doing so, it presses against the joint 123 and releases the blocking position. The magnetic force between the magnets 127, 130 is small or can be set to zero by controlling the preferably switchable magnets 127, 130, so that the magnetic force does not prevent the release of the blocking position.

[0045] The advantage of the blocking device 120 is that it allows for the individual setting of the time at which the discharge of the energy storage device 70 begins. The period between the end of the first phase (charging the energy storage device) and the beginning of the second phase (discharging the energy storage device) can be referred to as the holding or blocking phase.

[0046] In the second phase, the output rack 110 moves abruptly to the left, i.e., opposite to arrow 126. The output rack 110 meshes with a wear intermediate gear 140 arranged on the output shaft 40. A freewheel 150 is provided between the output intermediate gear 140 and the output shaft 40, which essentially has the same function as the first freewheel 50 in the previous embodiments. The freewheel 150 ensures that during the jerky movement of the output rack 110 to the left, the output intermediate gear 140 can transmit torque to the output shaft 40, while in the first phase (output rack 110 moves to the right) and in the holding phase (output rack 110 is stationary) the rotation of the output shaft 40 is not hindered by the output rack 110.

[0047] Fig. Figure 6 shows various embodiments of the invention. In the embodiment of Fig. 6A, the energy storage device 70 is designed as a weight that can be raised or lowered by the lever 61, which is non-rotatably connected to the output gear 30. The potential energy of the weight corresponds to the energy stored in the energy storage device.

[0048] Fig. Figure 6B essentially shows the embodiment of the Fig. 3 with the crank mechanism 90. By adjusting the size of the first angular range in which the drive gear 10 has the toothing 11 and / or by dimensioning the diameters of the gears 10, 30, the transmission can be adjusted so that the output gear 30 moves in the same direction of rotation in the first phase and the second phase. In one embodiment, the output gear 30 must rotate by at least 180° during the first phase.

[0049] Fig. Figure 6C illustrates that the drive gear 10 can also have a toothing 11 that extends over the entire circumference of the drive gear 10. Here, the toothing 11 and the toothing 31 of the output gear 30 are constantly meshing. Therefore, a second freewheel (not shown) is necessary to ensure that the drive shaft 20 does not decelerate the output gear 30 in the second phase, i.e., the phase in which the energy storage device is discharged. Fig. 7D illustrates that the output element can be designed as an output rack.

[0050] Fig. Figure 7 shows schematically the force curves of a transmission with four drive gears and four driven gears. The first phase of engagement between the drive gear and driven gear is 90° (see Fig. 7A) or 80° (see Fig. 7B). The angle of rotation of the drive gears is plotted on the horizontal axis. The individual force curve represents the force acting, for example, on piston 72 (see Fig. 1) or on the coil spring 79 (see Fig. 3) works.

[0051] Out of Fig. 7A shows that to charge an energy storage device, a rotation angle of 90° of the associated drive gear is required. The ascending branch of the respective force curve thus corresponds to the first phase in which the respective energy storage device is charged. Here, the force increases steadily, for example, to charge the coil spring 79 (see Fig. 3) to continue to tension. In the second phase, beginning directly after the first phase, spring 79 is released very quickly, causing the energy storage device to abruptly transfer energy to the output shaft. The phase difference between the drive gears here is 90°, resulting in an overlap of the force curves.

[0052] If a different gear ratio exists between the individual drive elements or drive gears 30 and the output shaft 40, the output shaft 40 can be accelerated successively. For this purpose, the highest gear ratio is assigned to the first force curve (0 to 90°) and the lowest gear ratio is assigned to the last force curve (270 to 360°).

[0053] Fig. Figure 7B shows that after tensioning the coil spring 79, it is held in this tensioned state for a certain time. This holding is achieved by the blocking device 120 described above (see Fig. 4 and Fig. 5) is possible, whereby each energy storage device is assigned a blocking device. The release of the respective blocking position of the individual blocking devices occurs at the same time (see Fig. 7B at 330°). The holding phase for the first charged energy storage unit is 250° (330° - 80°).

[0054] The embodiment of the Fig. 7B allows all energy storage devices to be discharged at the same time, which can generate a particularly strong impulse to drive the output shaft. List of reference symbols 1 gearbox 10 drive gear 11 Gearing 12 Direction of rotation / arrow 13 tooth 20 drive shaft 30 Output gear 31 Gearing 32 Direction of rotation / arrow 40 Output shaft 50 first freewheel 60 rods 61 levers 62 joint 63 Piston rod 64 Direction / Arrow 70 energy storage units 71 cylinders 72 pistons 73 Axis 74 displacement 75 compressed air 76 Line 77 Valve 78 Room 79 coil spring 80 Direction / Arrow 81 Adjustment mechanism 90 Crank drive 91 Crank 92 first connecting rod 93 second connecting rod 94 joint 95 joint 100 linear generators 110 Output rack 111 End 120 Blocking device 121 first bar 122 second bar 123 joint 124 pivot bearings 125 joint 126 Direction / Arrow 127 Magnet 130 release device 131 Magnet 132 release rod 133 cams 140 Output intermediate gear

Claims

[1] Gearbox (1) for generating a high-speed rotary motion from a low-speed rotary motion, comprising: - a drive shaft (20) rotating at low speed; - a drive wheel that sits on the drive shaft; - an output shaft (40) rotating at high speed; - an output element engaged with the drive gear, the engagement comprising a first phase in which the drive gear drives the output element and a second phase in which the drive gear and the output element are decoupled from each other; - an energy storage device (70) which, in the first phase of the engagement, absorbs energy by a movement of the output element and, in a second phase of the engagement, releases the absorbed energy via the output element to rotate the output shaft. [2] Transmission (1) according to claim 1, characterized bythat a first freewheel (50) is provided between the output element and the output shaft (40), so that the output element can only drive the output shaft (40) but cannot brake it. [3] Transmission (1) according to claim 2, characterized by that a second freewheel is provided so that the drive shaft (20) does not brake the output element in the second phase. [4] Transmission (1) according to one of claims 1 to 3, characterized by that the drive wheel is designed as a drive gear (10). [5] Transmission (1) according to claim 4, characterized by that the drive gear (10) has a first angular range with teeth and a second angular range without teeth. [6] Transmission (1) according to claim 5, characterized by that at least one edge tooth (13) of the first angular range is replaceable. [7] Transmission (1) according to one of claims 4 to 6, characterized bythat the output element is designed as an output gear (30) or as an output rack (110). [8] Transmission (1) according to one of claims 1 to 7, characterized by that the intervention further comprises a holding phase which is provided between the first phase and the second phase, wherein in the holding phase the release of the energy absorbed by the energy store (70) is blocked. [9] Transmission (1) according to claim 8, characterized by that a blocking device (120) is provided which, in a blocking position, blocks the release of the energy absorbed by the energy store (70). [10] Transmission (1) according to claim 9, characterized by that the blocking position can be released by a triggering device (130). [11] Transmission (1) according to claim 9 or 10, characterized bythat the blocking device (120) has two rods (121, 122) connected to one another by a joint (123) which lie essentially on a straight line in the blocking position. [12] Transmission (1) according to one of claims 1 to 11, characterized by that at least one further drive wheel is seated on the drive shaft (20), which is in engagement with a further output element. [13] Transmission (1) according to claim 12, characterized by that the first phase of the engagement between the drive wheel and the output element and a first phase of the engagement between the further drive wheel and the further output element are phase-shifted. [14] Transmission (1) according to one of claims 1 to 13, characterized by that the energy store (70) is assigned an adjusting mechanism (81) by means of which a resistance force to be overcome when filling the energy store (70) can be adjusted. [15] Transmission (1) according to one of claims 1 to 14, characterized bythat a linear generator (100) is provided, by means of which a linear movement generated by the output element is converted into electrical energy.

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