Gearbox with energy storage

Abstract

A transmission (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 mounted on the drive shaft; - an output shaft (40) rotating at high speed; - an output element engaged with the drive wheel, the engagement comprising a first phase in which the drive wheel drives the output element and a second phase in which the drive wheel and the output element are decoupled from each other; - an energy storage device (70) which, in the first phase of engagement, absorbs energy through movement of the output element and, in the second phase of engagement, releases the absorbed energy via the output element to rotate the output shaft.

Description

The invention relates to a transmission for generating a high-speed rotational movement from a low-speed rotational movement.A transmission of this type is known from DE 10 2012 000 341 A1. The transmission comprises a drive shaft and a drive wheel which is seated on the drive shaft. The drive shaft rotates at a comparatively low speed, as is the case here with a wind turbine with a slowly rotating rotor.It is further known that the drive gear in the form of a drive gear is in meshing engagement with an output element in the form of a driven gear which is seated on an output shaft. By selecting the diameters or the number of teeth of the two gears, a transmission ratio i of the transmission can be set. The transmission ratio i corresponds to the ratio of the diameter of the driven gearwheel to the diameter of the drive gearwheel (i=dAbtrieb / d Antrieb). By selecting a large diameter for the drive gear paired with a small diameter of the driven gear, very high rotational speeds of the output shaft can be realized even if the drive shaft rotates only slowly. However, only a low torque is available on the rapidly rotating output shaft. The transmission losses can also be high if a particularly low transmission ratio (i<<1 or rotational speed n Antrieb<< rotational speed nWd) is required.WO 2019 / 166237 A1 discloses a transmission with a drive gear and a driven gear, wherein the driven gear is rotated and at the same time its axis of rotation is displaced. This leads to higher rotational speeds of the driven gearwheel without the diameter of the driven gearwheel having to be small than the diameter of the drive gearwheel.WO 2017 / 012902 A1 discloses a transmission with an input shaft, an output shaft, a clutch wheel and a supporting device, wherein the clutch wheel is connected to the output shaft via a torsion spring and wherein means are provided for coupling the clutch wheel to the input shaft or to the supporting device for a few milliseconds in each case.DE 10 2015 103 928 A1 and DE 296 23 149 U1 disclose a transmission with a drive shaft, an output shaft and an energy store. The energy store has a clamping element which is clamped by the drive shaft and delivers the stored energy to the output shaft.The object of the invention is therefore to provide an efficient transmission which, in the case of a slowly rotating drive shaft, enables a high rotational speed of the output shaft and, at the same time, high torques on the output shaft.The object on which the invention is based is achieved with the combination of features according to claim 1. Embodiments of the invention can be taken from the dependent claims relating to claim 1.According to the invention, it is provided that the engagement comprises a first phase and a second phase, wherein in the first phase the drive wheel drives the output element and in a second phase the drive wheel and the output element are decoupled from one another. The transmission comprises an energy store 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, outputs the absorbed energy via the output element for rotation of the output shaft.The energy absorbed by the energy store can be discharged abruptly, so that high torques are present temporarily at the output shaft at high rotational speeds at the same time. It is thus possible, for example, to further accelerate an already rapidly rotating flywheel with the output shaft.In the second phase, the drive wheel and the output element are decoupled from one another. Decoupling means here that the output element can move freely and as fast as possible for driving the output shaft without the drive gearwheel representing an obstacle for the output shaft.The first phase and the second phase form a cycle which is repeated continuously 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 configured 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. The cycle can comprise further phases in addition to the first phase and the second phase, which will be discussed in more detail later.The energy store can have a helical spring which is tensioned in the first phase of the engagement. In the second phase, the helical spring relaxes and emits energy in a relatively short time, which is used to drive the output shaft. Alternatively or additionally, the energy store can have a cylinder with a piston and a displacement chamber in which a gaseous fluid is located. In the first phase, the piston is moved in the cylinder, so that the stroke space is reduced and the gaseous fluid is compressed. In the second phase, the pressure in the displacement chamber is used to displace the piston at a relatively high speed and force for driving the output shaft.A first freewheel can be provided between the output element and the output shaft, so that the output element can drive the output shaft, but cannot brake or block it. The first freewheel can be designed in such a way that in the first phase, in which the energy store is filled, no torque or no force is transmitted from the output element to the output shaft. In the second phase, the first freewheel provides for a torque transmission or force transmission from the output element to the output shaft.In one exemplary embodiment, a second freewheel is provided, such that the drive shaft does not brake the output element in the second phase. The second freewheel ensures that torque or force transmission between the output element and the drive wheel is saturated only in the first phase.The drive wheel can be formed as a drive wheel. The drive gear may 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 remainder of the entire 360° of the drive gear.The output element can be formed as an output gearwheel. The driven gear is in meshing engagement with the drive gear at least in the first phase of the engagement. If, for example, the first angular range of the drive gearwheel extends over 90° and the driven gearwheel is a spur gear with a toothing over the entire circumference, the first phase of the engagement extends only over a quarter of the full revolution of the drive gearwheel. At three quarters of the full revolution of the drive gearwheel, no torque transmission takes place from the drive gearwheel to the driven gearwheel, since in this angular range the teeth necessary for the torque transmission are missing from the drive gearwheel. During this time, in which no meshing engagement is established between the drive gearwheel and the driven gearwheel, the second phase of the engagement in which the energy store is discharged preferably falls. The second phase can be shorter than the time of the non-existing meshing engagement between the drive gearwheel and the driven gearwheel.In one exemplary embodiment, the output element is designed as an output toothed rod. In the first phase of the engagement between the drive gear and the driven rack, a rotation of the drive gear results in a preferably linear movement of the driven rack. The linear movement of the output rack can, for example, tension a helical spring of the energy store.At least one edge tooth of the first angular range of the drive gear may be interchangeable. The edge tooth is a tooth of the toothing of the first angular range, which directly adjoins the second angular range without toothing. Due to the edge position, the edge tooth must absorb particularly high forces in the first phase of the engagement, since a distribution of forces to a plurality of teeth, as is the case in a central region of the first angular range, is not possible. The rim tooth is preferably made of a hardened material. In addition, a further edge tooth of the first angular range, now arranged at the end of the first angular range, can also be interchangeable.An edge tooth or an outer tooth of the drive toothed rod can also be replaceable and / or made of hardened material. Here too, the consideration is based on being able to replace the tooth or the teeth of the toothing which are exposed to particular loads during operation of the transmission or to be designed to be particularly resistant.The engagement can furthermore have a holding phase which is provided between the first phase and the second phase, wherein the output of the energy absorbed by the energy store is blocked in the holding phase. This means that after the end of the first phase, the energy in the energy store is not used directly for driving the output shaft, but remains in the energy store over the period of the holding phase and is only released with a time delay after the expiration of the first phase.The transmission can comprise a blocking device which, in a blocking position, blocks the discharge of the energy absorbed by the energy store. The blocking device thus represents a possibility for realizing the holding phase in which the energy store is charged but not yet discharged.The blocking position can be canceled by a release device. The triggering device can have a magnet or an actuatable adjusting element which switches after a certain time has elapsed and thus cancels the blocking position. If the blocking position is canceled, a discharge of the energy store for driving the output shaft is possible.The blocking device can have two rods connected to one another by a joint, which in a blocking position preferably lie substantially on a straight line. In the blocking position, the two rods form a buckling rod which prevents a movement of the output element only when the two rods lie on a straight line. The triggering device can be designed here to exert a small laterally acting force on the joint during triggering, by which force the joint is deflected. The two rods then buckle laterally away and no longer provide resistance to the movement of the output member.At least one further drive wheel can be seated on the drive shaft, which is in engagement with a further output element. Preferably, three, four, five or more than five driving wheels are used in order to make it possible to smooth the drive of the output shaft. For this purpose, the first phase of the engagement between the drive gearwheel and the output element and a first phase of the engagement between the further drive gearwheel and the further output element are preferably phase-shifted. In the case of a total of four drive gears, for example, the phase shift is preferably 90°.The energy store can be assigned an adjustment mechanism by means of which a resistance force to be overcome when the energy store is filled can be adjusted. In addition, a linear generator may be provided, by which a linear movement generated by the movement of the output element is converted into electrical energy.The invention is explained in more detail with reference to the exemplary embodiments shown in the drawing. The following are shown: FIG. 1 shows a transmission according to the invention with an energy store; FIG. 2 shows a transmission according to the invention with a plurality of drive wheels; FIG. 3 shows a transmission according to the invention with a linear generator; FIG. 4 shows a transmission according to the invention with a blocking device; FIG. 5 shows the transmission of FIG. 4 from above; FIG. 6 shows further exemplary embodiments of the invention; and FIG. 7 shows various curves of the force acting on the energy store.FIG. 1 shows a transmission, which is denoted in its entirety by 1. The transmission 1 comprises a drive wheel in the form of a drive wheel 10 which is seated on a drive shaft 20. The drive gear 10 has a toothing 11 which 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 gearwheel 10.The transmission 1 furthermore comprises an output element in the form of an output gearwheel 30 with a toothing 31 which extends over the entire circumference of the output gearwheel 30. The abrasion gear 30 is seated on an output shaft 40. A freewheel 50 is provided between the output shaft 40 and the output gear 30, which freewheel is also referred to here as the first freewheel. Its function will be described below.The transmission 1 also comprises a linkage 60 and an energy store 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 pivotally connected to each other via the joint 62. The lever 61 is connected to the driven gearwheel 30 in a rotationally fixed manner. If the drive gear rotates clockwise (see arrow 32), the lever 61 and thus, via the joint 62, the piston rod 63 is moved upwards in the illustration of FIG. 1 (see arrow 64).The energy store 70 has a cylinder 71 and a piston 72, which is mounted displaceably along the longitudinal axis of the cylinder 71. The cylinder 71 is rotatably fixed to an axle 73 so that the cylinder can swivel about the axle 73 so that the linkage 60 is not blocked upon rotation of the output gear 30. The piston 72 is connected to the piston rod 63 and defines with the cylinder 71 a displacement space 74 in which compressed air 75 is located. Air can be supplied to the displacement chamber 74 or removed via a line 76 which is connected to the displacement chamber 74, controlled by a valve 77. The valve 77 can therefore be used to set the force which has to be overcome in order to charge the energy store or which acts on the piston rod 63 when the energy store is discharged. A space 78 below the displacement space 74 is in communication with the environment. There correspondingly prevails ambient pressure.The drive gear 10 is meshed with the driven gear 30. The engagement has a first phase in which the drive gearwheel 10 drives the driven gearwheel 30. In the embodiment of FIG. 1, the first phase is characterized by the meshing engagement between the toothing 11 of the drive gearwheel 10 and the toothing 31 of the driven gearwheel 30, and in this meshing engagement a rotation of the drive gearwheel 10 in the counterclockwise direction (see arrow 12) results in a rotation of the driven gearwheel 30 in the clockwise direction (see arrow 32). FIG. 1 shows the gears 10, 30 in an angular position at the end of the first phase. Further progress of the rotation of the drive gear 10 results in the meshing engagement between the drive gear 10 and the driven gear 30 no longer being established. The first phase of the engagement is thus followed by a second phase of the engagement, in which the driven gearwheel 30 is no longer driven by the drive gearwheel 10. Since, in the second phase of the engagement, the drive gearwheel 30 can no longer be supported on the drive gearwheel 10, the pressure acting on the piston 72 in the stroke chamber 74 has the effect that the piston 72 and therefore the piston rod 63 are moved downward, that is to say counter to the arrow 64. The lever 61 is pivoted downward in the counterclockwise direction and thereby rotates the output gear 30 in the counterclockwise direction. The freewheel 50 is designed in such a way that the torque acting on the drive gearwheel 30 is transmitted to the output shaft 40 in this rotational direction. As a result of the abrupt release of the pressure in the displacement chamber 74, the output shaft 40 experiences a strong rotational acceleration with a comparatively large torque. The second phase of the engagement therefore represents the period of time during which the output shaft is driven by discharging the energy store.If, for example, the drive shaft 10 rotates at a speed of 15 U / min, then a full rotation of the drive shaft 20 takes four seconds. Since the first angular range with the toothing 11 extends over a quarter of the circumference, the length of the first phase in which the drive gearwheel 10 drives the driven gearwheel 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 store 70 is discharged is significantly shorter. In one embodiment, the second phase is at least a factor of 3 shorter than the first phase (e.g., 250 ms).Assuming that the drive shaft 20 rotates substantially at a constant rotational speed (for example, at the above 15 U / min), the second phase of engagement includes a waiting phase in which no meshing engagement is established between the gears 10, 30. In this waiting phase, the drive gearwheel 30 is stationary until the toothing 11 of the drive gearwheel 10 comes into contact with the toothing 31 of the driven gearwheel 30 again. At an assumed rotational speed of 15 U / min, the waiting time in the exemplary embodiment of FIG. 1 is somewhat less than three seconds. The almost three seconds result from the difference in time for one full revolution 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.The freewheel 50 makes it possible that, when the output gearwheel 30 is stationary, the output shaft 40 can continue to rotate in the counterclockwise direction in the waiting phase. In the waiting phase, no torque is transmitted between the output gear 30 and the output shaft 40. Only when, in the second phase of a subsequent cycle, the angular speed of the output gearwheel 30 is greater than the angular speed of the output shaft 40, the freewheel 50 ensures the torque transmission required for driving 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 speed up the output shaft 30.FIG. 1 shows two teeth 13, 33 stored in black, which are subjected to a particularly high load because of their position in the toothing 11 or 13. It can be provided that these teeth 13, 33 are replaceable and / or specially hardened.FIG. 2 shows a further exemplary embodiment, wherein here the drive shaft 20 and the output shaft 40 are illustrated in a plan view. In addition to the drive gearwheel 10 already described above, further drive gearwheels 10 aare seated on the drive shaft 20, and further driven gearwheels 30 aare arranged on the output shaft 40 in addition to the driven gearwheel 30. The cooperation of the drive gearwheel 10 aand the driven gearwheel 30 acorresponds to the above-described cooperation of the drive gearwheel 10 and the driven gearwheel 30, and correspondingly each pair of the drive gearwheel 10 aand the driven gearwheel 30 acan be assigned a linkage 60 aand a freewheel 50 a. The first phase of engagement between drive gear 10 and driven gear 30 is out of phase with a first phase of engagement between driven gear 10 aand driven gear 30 a. In the case of the total of five drive gears 30, 30 ain this case, the phase shift between the individual first phases is preferably 72° (360° / 5). This phase shift ensures a more continuous rotation of the drive shaft 20 and the output shaft 40. the phase shift makes it possible to prevent the drive shaft 20 from temporarily rotating without load, since there is always a gearwheel pair of drive gearwheel / output gearwheel which is in the first phase.As explained above, in the exemplary embodiment of FIG. 2, the output gears 30, 30 aare seated on the output shaft 40, wherein in the second phase the corresponding output gear 30 rotates at the same rotational speed as the output shaft 40.FIG. 3 shows a further exemplary embodiment of the transmission according to the invention. Components or details which are similar or identical to components or details of the exemplary embodiment of FIG. 1 are provided with the same reference numerals. This also applies analogously to all further figures. In the following description of the figures, the differences from the exemplary embodiment of FIG. 1 are discussed in particular.The output gearwheel 30 and the energy store 70 are connected here via a crank drive 90 to a crank 91, a first connecting rod 92 and a second connecting rod 93. A further joint 95 provides an articulated connection between the first connecting rod 91 and the second connecting rod 93 The energy store 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 operation 90 is actuated, wherein the second connecting rod 93 is moved upward and downward parallel to the longitudinal axis (see arrow 80) of the helical spring 79. In the first phase of the engagement between the drive gearwheel 10 and the driven gearwheel 30, the helical spring 79 is tensioned, the energy store 70 absorbing energy in the process. In the second phase of the engagement, this energy is dissipated again in order to drive the output shaft 40 with the output gearwheel 30. A prestress of the spring 79 can be adjusted by means of an adjustment mechanism 81. The actuating mechanism 81 has the same function as the valve 77 in the exemplary embodiment of FIG. 1. the actuating mechanism 81 can be used to set the force which has to be overcome for charging the energy store 70 or which is available during discharging of the energy store 70.The output shaft 40 may be connected to a generator for power generation. Additionally or alternatively, a linear generator 100 is provided, by means of which current can be generated when the second connecting rod 93 is displaced within the linear generator 100 along the arrow 80.Instead of the linear generator 100 or in addition, a piston-cylinder unit with a displacement chamber can be provided which abruptly increases its volume in the second phase. The displacement chamber can be connected to a line through which a gaseous fluid flows, which cools down due to the sudden increase in volume. If the fluid is a liquid fluid, it can evaporate as a result of the sudden increase in volume and thus draw heat from the environment of the piston-cylinder unit. The piston-cylinder unit can thus be operated as a refrigerating machine.FIGS. 4 and 5 show a further exemplary embodiment of the invention. FIG. 4 shows the transmission 1 from the side, FIG. 5 the transmission from above. The output element is here formed as an output toothed rod 110. FIGS. 4A and 4B show the drive rod 110 in different axial positions.The drive rack 110, similar to the second connecting rod 93 of the embodiment of FIG. 3, is coupled to the energy storage device 70 and the linear generator 100. An axial displacement of the output toothed rod 110 thus leads to a loading or unloading of the energy store 70.FIG. 4A shows the engagement between the drive gear 10 and the driven rack 110 at the beginning of the first phase. The drive gearwheel 10 rotates counterclockwise (see arrow 12) and is already in meshing engagement with the toothing of the driven rack 110, with a tooth of the toothing 11. The rotary movement of the drive gearwheel 10 moves the driven toothed rack 110 to the right in the illustration of FIG. 4 and charges the energy store 70 (for example by tensioning a helical spring). At an end 111 facing away from the energy store 70, the output toothed rack 110 is connected to a blocking device 120.The blocking device 120 comprises 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 fixed pivot bearing 124. An end of the second rod 122 facing away from the joint 123 is connected in an articulated manner to the abrasion toothed rod 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 be 180° (see FIG. 5B ). The position shown in FIG. 5B can also be referred to as the end position, since a further displacement of the output toothed rack 110 in the direction 126 is not possible. In the end position shown, the rods 121, 122 lie on a straight line. Insofar as the rod 121, 122 are not deflected out of this end position, they block the output toothed rod 110 from springing back and thus the energy store 70 from discharging.In order to stabilize the blocking position, the blocking device 120 has a magnet 127 which interacts with a magnet 131 of a triggering device 130. The magnets 127, 131 have the effect that the blocking position does not break down unintentionally and the energy store 70 is discharged unintentionally. The trip device 130 includes a trip bar 132 that cooperates with a rotatable cam 133. The rotation of the cam 133 allows the release rod 132 to be axially displaced. In this case, it presses against the joint 123 and lifts the blocking position. The magnetic force between the magnets 127, 130 is small or can be set to zero by actuating the preferably switchable magnets 127, 130, so that the magnetic force does not oppose the release of the blocking position.The advantage of blocking device 120 is to individually define the time at which the discharge of energy store 70 begins. The time period between the end of the first phase (charging of the energy store) and the beginning of the second phase (discharging of the energy store) can be referred to as the holding or blocking phase.In the second phase, the output toothed rack 110 moves abruptly to the left, that is to say opposite the arrow 126. The output rack 110 meshes with an intermediate wear gear 140 disposed on the output shaft 40. Between the output intermediate gear 140 and the output shaft 40 there is provided a freewheel 150 which has substantially the same function as the first freewheel 50 in the preceding exemplary embodiments. The freewheel 150 ensures that, during the jerking movement of the output toothed rack 110 to the left, the output intermediate gear 140 can transmit torque to the output shaft 40, while in the first phase (output toothed rack 110 moves to the right) and in the holding phase (output toothed rack 110 is stationary), the rotation of the output shaft 40 is not hindered by the output toothed rack 110.FIG. 6 shows various embodiments of the invention when viewed together. In the exemplary embodiment of FIG. 6A, the energy store 70 is designed as a weight which can be raised or lowered by the lever 61 which is connected to the output gearwheel 30 in a rotationally fixed manner. The potential energy of the weight corresponds here to the energy charged in the energy store.FIG. 6B substantially shows the exemplary embodiment of FIG. 3 with the crank drive 90. For this purpose, in one exemplary embodiment, the output gearwheel 30 must rotate by at least 180° during the first phase.FIG. 6C is intended to illustrate that the drive gearwheel 10 can also have a toothing 11 which extends over the entire circumference of the drive gearwheel 10. Here, the toothing 11 and the toothing 31 of the output gearwheel 30 are constantly in meshing engagement. Therefore, a second freewheel (not shown) is necessary, which ensures that the drive shaft 20 does not brake the output gearwheel 30 in the second phase, that is to say in the phase in which the energy store is discharged. FIG. 7D illustrates that the output element may be formed as an output rack.FIG. 7 schematically shows the force profiles of a transmission with four drive gearwheels and four driven gearwheels. The first phase of engagement between the drive gear and the driven gear is 90° (see FIG. 7A ) and 80° (see FIG. 7B ), respectively. The horizontal axis represents the angle of rotation of the drive gears. The individual force profile represents the profile of the force which acts, for example, on the piston 72 (see FIG. 1 ) or on the helical spring 79 (see FIG. 3 ).FIG. 7A shows that a rotation angle of 90° of the associated drive gearwheel is necessary in each case for charging an energy store. The ascending branch of the respective force profile thus corresponds to the first phase in which the respective energy store is charged. Here, the force increases steadily to further tension the coil spring 79 (see FIG. 3 ), for example. In the second phase, beginning directly following the first phase, the spring 79 is relaxed very quickly, as a result of which the energy store abruptly outputs energy to the output shaft. The phase difference between the drive wheels is 90° here, so that the force profiles are superimposed.If a different transmission ratio is respectively provided between the individual drive elements or drive gearwheels 30 and the output shaft 40, the output shaft 40 can be successively accelerated. For this purpose, the first force profile (0 to 90°) is assigned the greatest transmission ratio and the last force profile (270 to 360°) is assigned the smallest transmission ratio.FIG. 7B shows that after the tensioning, the helical spring 79 is held in this tensioned state for a certain time. This holding is possible by the blocking device 120 described above (see FIGS. 4 and 5 ), wherein a blocking device is assigned to each energy store. The release of the respective blocking position of the individual blocking devices takes place here at the same time (see FIG. 7B at 330°). The holding phase for the energy store charged first is 250° (330°-80°) here.The embodiment of FIG. 7B allows all energy stores to be discharged at the same time, whereby a particularly strong impulse for driving the output shaft can be generated.List of reference characters1 Transmission 10 Drive gearwheel 11 Toothing 12 Direction of rotation / arrow 13 Tooth 20 Drive shaft 30 Driven gearwheel 31 Toothing 32 Direction of rotation / arrow 40 Output shaft 50 First freewheel 60 Linkage 61 Lever 62 Joint 63 Piston rod 64 Direction / arrow 70 Energy store 71 Cylinder 72 Piston 73 Axis 74 Displacement 75 Compressed air 76 Line 77 Valve 78 Space 79 Helical spring 80 Direction / arrow 81 Adjusting mechanism 90 Crank drive 91 Crank 92 First connecting rod 93 Second connecting rod 94 Joint 95 Joint 100 Linear generator 110 Driven rack 111 End 120 Blocking device 121 First rod 122 Second rod 123 Joint 124 Rotary bearing 125 Joint 126 Direction / arrow 127 Magnet 130 Triggering device 131 Magnet 132 Triggering rod 133 Cam 140 Driven intermediate gear

Claims

A transmission (1) for generating a high speed rotational movement from a low speed rotational movement, comprising: - a drive shaft (20) rotating at low speed; - a drive wheel seated on the drive shaft; - an output shaft (40) rotating at high speed; - an output element engaged with the drive wheel, the engagement comprising a first phase in which the drive wheel drives the output element and a second phase in which the drive wheel and the output element are decoupled from one another; - an energy store (70) which in the first phase of engagement absorbs energy by a movement of the output element and in the second phase of engagement outputs the absorbed energy via the output element for rotation of the output shaft.Transmission (1) according to Claim 1, characterized in that a first freewheel (50) is provided between the output element and the output shaft (40), with the result that the output element can only drive the output shaft (40), but cannot brake it.Transmission (1) according to Claim 2, characterized in that a second freewheel is provided, with the result that the drive shaft (20) does not brake the output element in the second phase.Transmission (1) according to one of Claims 1 to 3, characterized in that the drive wheel is designed as a drive gearwheel (10).Transmission (1) according to Claim 4, characterized in that the drive gearwheel (10) has a first angular range with teeth and a second angular range without teeth.Transmission (1) according to Claim 5, characterized in that at least one edge tooth (13) of the first angular range is replaceable.Transmission (1) according to one of Claims 4 to 6, characterized in that the output element is designed as an output gearwheel (30) or as an output toothed rod (110).Transmission (1) according to one of Claims 1 to 7, characterized in that the engagement furthermore has a holding phase which is provided between the first phase and the second phase, wherein the output of the energy absorbed by the energy store (70) is blocked in the holding phase.Transmission (1) according to Claim 8, characterized in that a blocking device (120) is provided which, in a blocking position, blocks the discharge of the energy absorbed by the energy store (70).Transmission (1) according to Claim 9, characterized in that the blocking position can be cancelled by a release device (130).Transmission (1) according to Claim 9 or 10, characterized in that the blocking device (120) has two rods (121, 122) which are connected to one another by a joint (123) and which, in the blocking position, lie substantially on a straight line.Transmission (1) according to one of Claims 1 to 11, characterized in that at least one further drive wheel is seated on the drive shaft (20), said further drive wheel being in engagement with a further output element.Transmission (1) according to Claim 12, characterized in 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.Transmission (1) according to one of Claims 1 to 13, characterized in that the energy store (70) is assigned an adjustment mechanism (81) by means of which a resistance force to be overcome when the energy store (70) is filled can be adjusted.Transmission (1) according to one of Claims 1 to 14, characterized in that a linear generator (100) is provided, by means of which a linear movement generated by the output element is converted into electrical energy.

Images