DE3243849C1 - Device for equalising irregular rotational energy - Google Patents

Abstract

In order to equalise the irregular rotational energy of a screw or propeller shaft driven by the wind or a flow of water and transmit it to a uniformly rotating output shaft stabilised with a flywheel, the invention proposes to take off in a pulsed manner the energy arising at the input of the device and to transmit it via a linkage and a spring arrangement to the output shaft, the output shaft being provided with a crank drive which, by its respective position, determines when an energy pulse is to be taken off and transmitted. In this way, it is ensured that the energy pulses are used in the optimum manner at the crank drive at the output shaft and assist the connecting rod in its already existing movement.

Description

First and foremost, the device according to the invention is intended to in places far from civilization with the help of the wind or by means of the current a torrent or the like. To gain energy. With the help of a propeller or a propeller exposed to the flow of water can in a manner known per se an input shaft, where it is then of great importance that to equalize existing rotational energy on the input shaft and to a To transmit output shaft, with which a work machine or a generator can drive To solve the aforementioned problem, the device is the introductory one said type characterized in that the input shaft carries a sprocket, that the output shaft is connected to a crank mechanism, that an energy pulse transmitting connection between input shaft and output shaft from a next the circumference of the sprocket arranged axially parallel to the camshaft, one of the Camshaft borne, from a waiting position between the rungs of the Sprossenrades movable, energy-absorbing cam arm, one of the camshaft drivable plunger with the plcuel rod connecting spring arrangement consists. and that there is a trigger that detects the position of the crank mechanism. the about a control for the engagement of the cam arm between the rungs of the sprout wheel and thus for a rotation of the camshaft, for the pulse-like impact des plunger, for tensioning the Fcdcranordnung and supporting the plcuelstangen movement cares.

Preferably, the spring assembly activated by the plunger includes two Storage springs that are controlled by the rotation of the crankshaft and are force-locked one after the other be connected to the connecting rod in such a way that one of the springs is between the dead centers pressing the crank and pulling the other of the springs is effective.

Further details and features of the invention emerge from the Subclaims.

An exemplary embodiment of the Subject of the application illustrated in more detail. In the drawings, Fig. 1 shows a schematic side view of the power transmission device according to the invention, F i g. 2 is a schematic plan view of FIG. 2, fig. 3 is a schematic plan view on the force-reducing cam, FIG. 4 is a schematic plan view of the force-emitting Cam, Fig. 5 shows a schematic plan view of the control cam in connection with FIG the control linkage, F i g. 6 shows an enlarged detail of FIG. 1 in side view, F i g. 7 is a schematic side view of the FIG. 1 shown Disconnection device in a compared to FIG. 5 plane offset by 90 °, FIG. 8 a schematic side view of the connecting rod arrangement for driving the rotor, F i g. 9 shows a cross section to FIG. 8 according to the section line IX-IX and FIGS. 10-13 Details of the interlock control provided on the rotor.

The schematic overall view of the power transmission device according to the invention in Fig. 1 and 2 show a force-introducing shaft 102, for example the irregularly driven drive shaft of a wind turbine or one by a water current driven screw can be. Assume that the shaft 102 is in direction of the arrow 101 shown rotates. With the irregular rotating energy According to the object of the invention, the shaft 102 is intended to be an electric generator 19 are driven at a substantially uniform speed.

Via a belt drive 131 or via an intermediate gear transmission the generator 19 is to be driven by a rotor 20, which is is a flywheel with a relatively large mass.

The essence of the present invention is that the force-introducing Sprout wheel 2 on shaft 102 is not permanently coupled to the axis of rotor 20 is, but the rotor 20 is the respective existing input energy, controlled by Operating state of the rotor 20, receives pulses. In other words, this means that the run of the rotor 20 determines when it is different from the one with changing speeds running drive wheel 2 energy is supplied.

The drive wheel 2 is two firmly connected to one another Discs and rungs 1 arranged between the discs, from which the energy is removed. A camshaft mounted at 33 is axially parallel to the drive shaft 102 6 arranged, the axially one behind the other three two-armed, symmetrically formed Has cams, namely a force-absorbing cam 32, a force-emitting cam 5 and a control cam 4. All three cams are non-rotatably connected to the camshaft 6.

The force decreasing cam 32 is arranged so that they over the Edge can engage in the sprocket 2 between the individual rungs 1. As the F i g. 3 shows, the cam 32 is in the rest state so that it the rungs 1 not acted upon, so that the wheel 2 can run freely. When the cam 32 in subsequent is moved into the circumference of the Sprossenrades 2 in a manner still to be described, can one arm of the two-niigelig formed cam 32 on the next penetrate exposed gap between the rungs 1. So that the cam 32 does not accidentally act on a rung 1 of the drive wheel 2 with its tip 145 in the middle can, are, as F i g. 1 shows the rungs up over the top side panel extended. These extensions of the rungs 1 work with the means of a compression spring 105 supported pivot arm 103 together. so that each pending drive Rung 1 of the cam 32 is passed rolling.

The outward movement of the pivot arm 103 mounted at 104 is limited with a stop 146 so that the rungs 1 just about the swivel arm 103 can touch.

The next to the force-reducing double cam 32 on the camshaft 6 arranged control cam 4 is also with two opposite arms Mistake. This control cam 4 receives in a manner to be described below a control pulse from the rotor 20, which the cam 4 and with this the camshaft 6 and the double cam 32 rotates so far that it is of the in F i g. 3 with extended Lines shown position in the position shown with dashed lines got.

As shown in FIG. 5, the cam 4 works with a feeler wheel 108 together, which at the end of a translationally displaceable in roller bearings 37, rod 31 preferably formed with a rectangular cross-section. This rod 31 is surrounded by a helical compression spring 35, which is on the one hand on one of the stationary bearing 37 of the rod 31 is supported and a spring abutment at the opposite end 38 is applied, which is firmly connected to the rod 31.

The spring abutment 38 therefore tensions the spring 35 whenever the feeler wheel 108 is acted upon from the outer end of the control cam 4.

Like F i g. 5 also shows the spring abutment 38 also works together with a pawl 29, the mode of operation of which will be discussed below will. The spring 35 is in the position of the control cam 4 shown in the drawing tense. If now in a manner to be described below, the pawl 29 in Roller bearings is moved translationally upwards, the spring 35 can relax, so that the control rod 31 moves to the left and the cam with the feeler wheel 108 rotated clockwise so far that the previously described force-absorbing Double cam 32 comes into engagement with the sprocket 2. By twisting the Double cam 32 over an angular path of approximately 1800 is then also the control cam 4 further rotated until after a distance of 180 ° it returns to the position according to FIG. 5 occupies. With this further movement of the double cam 4, the control rod 31 moved to the right again and the spring 35 is tensioned and collapsed again by means of the The pawl 29 is held in a tensioned position until another force pulse is received from the sprout wheel 2 can be found. So that the pawl 29 does not get caught in the spring 35 is located on the spring abutment 38 a corresponding cover on which the front end the pawl 29 can slide. When the pawl 29 is retracted is determined the rotor 20 in a manner still to be described below.

The one with a locking device is used to switch off the power transmission 9 provided angle lever 8 with the handle 141. In the shut-off position shown in FIG blocks the articulated at 39 on the lever 8 locking rod 140 the return movement of the Control rods 3i (Fig. 7).

The third cam 5 fixedly connected to the camshaft 4 is the 4 shown enlarged, also two-winged power-emitting Cam 5.

This cam 5 is ultimately responsible for the rotor 20 a drive on the rotor shaft 17 by means of the crank arm 21 and the connecting rod 22 receives. The power-emitting cam 5 works with a pivot lever 7, which carries a feeler roller 111 supported on the cam 5 and around a fixed bearing 112 can pivot. One arranged on the opposite arm of the pivot lever 7 Tension spring 113 ensures that the feeler roller 111 is constantly in contact with the cam 5 remain. If by rotating the camshaft 6 in the manner described above, the pivot lever 7 is moved up and down, there is an up and down movement of the translational movably mounted plunger 11, which is with a feeler roller 114 on an outer edge of the pivot lever 7 can support. The feeler roller 111 can be of a fork shape formed end part of the pivot lever 7 are carried. Since the feeler roller 114 is arranged on the tappet 11 opposite the camshaft 6, corresponds to the tappet stroke essentially the difference between the maximum and minimum transverse dimensions the cam 5. The rest position of the force-lifting cam 5 is defined by a Central depression or depression 125 into which the feeler roller 111 can fall. In In this last-mentioned position, the control cam 4 is in the position shown in FIG. 5 defined position shown, in which the force-absorbing cam 32, the in Fig. 3 assumes the position shown. These last-mentioned positions should hereinafter referred to as waiting position. Leaving the waiting position controls the rotor 20 in each case in a manner to be described below.

Like F i g. 2 shows that the pivot lever 7 is moved in a translatory manner The plunger 11 is mounted in two roller bearings 10. Also on the one remote from the camshaft 6 At the end of the plunger 11 carries a feeler roller 115, which via an interposed Swivel lever 28 transmits the translational movement of the plunger 11 to a roller 116, which is located on a pivot arm 27 which is mounted stationary at 117. So results When the plunger 11 moves back and forth, the arm 27 is pivoted the bearing 117. A spring 118 between the pivot arm 27 and the outer one Arm of the double-armed pivot lever 28 is a tension spring 118, which ensures that the feeler roller 115 constantly acts on the pivot lever 28.

The swivel arm 27 is used to store the data transmitted via the plunger 11 Thrust in a double spring arrangement 14, 14 '.

The spring arrangement consists of helical compression springs 14, 14 ', which store the energy transmitted by the plunger 11 until this energy is released from the Rotor 20 is requested controlled. The spring 14 shown below in FIG. 1 is supported 8 and 9 show, on the one hand, a spring abutment 26, wclchcs is connected to the connecting rod 22, and on the other hand to the connecting rod guide 34 from. The guide 34, which is a sliding hole for the rear end of the connecting rod 22 has is mounted on the pivot arm 27 such that the connecting rod 22 accordingly the rotational movement of the crank arm 21 can cover the required angular path. The interposition of the springs 14 can never lead to a sudden Acting on the connecting rod 22 come because the springs 14, 14 'are steady tense and only steadily release the pressure energy stored there again.

At the end of the connecting rod 22 is located for support on the rear of the pivot arm 27 an abutment 40. The connecting rod guide 34 is with her Roller bearing 36 mounted in the pivot arm 27 with bearing journals 41 which are in bearing bores 42 rest (Fig. 9).

The compression spring 14 'opposite the spring 14 is supported on the one hand on a stationary component 119 and on the other hand on a spring abutment 13, which is located at the outer end of the swivel arm 27. The springs 14 and 14 'work alternately during operation over half a revolution of the crank arm 21.

If, with the rotor 20 rotating, the shaft 17 and with it too As the crank arm 21 rotates, the crank pin 120 moves the connecting rod 22 in one sector defined by the crank arm length back and forth. This movement can be at Control of a power transmission pulse by means of the springs 14 and 14 ' stored strength will be strengthened. The springs 14 and 14 'will move forward of the plunger 11 by means of the rollers 115 and 116 of the pivot lever 28 and the pivot arm 27 excited.

In the one relating to FIG. 1 pivoted furthest to the right Position of the pivot arm 27 is this in a manner to be described below locked.

The upper spring remains in this fixed or locked position 14 'under tension while the lower spring 14 can expand around the crank arm 21 to rotate up to the upper gate point of the crank arm 21; When the connecting rod 22 is advanced in the connecting rod guide 34 by means of the spring 14 that the rotor 20 is in its top dead center (crank pin 120, axis 17 and pin 41 on a line) and the abutment 40 on the locked swivel arm 27 comes to rest, an unlocking is made so that the spring 14 'the Swivel arm 27 can move back, and the connecting rod 22 is effective pulling and the crank arm 21 can move from top dead center to bottom dead center.

As soon as the pivot arm 27 and the connecting rod 22 their return movement have completed, these components are also on hold again, in which the crank arm 21 and connecting rod 22 are back and forth unloaded by spring forces move forward and the rotor 20 can rotate.

The above locking and unlocking of the swivel arm 27 happens as follows: As F i g. 2 and 13 reveal that the horizontally aligned one is at rest Shaft 17 of rotor 20 in bearings 153.

Next to the upper bearing 153 (Fig. 2) is the pulley for the belt drive 131 via which the generator 19 is driven.

Located on the longer hub part of the rotor shaft 17 On the one hand, the pressure pulse trigger 18 and, on the other hand, the Schwenkal m-Entrieglel 16.

FIG. 2 in conjunction with FIG. 12 shows that the free end provided with a feeler roller pressure pulse trigger 18 whenever the crank pin 120 is at the bottom dead center in a manner to be described below Way for a release of the spring abutment 38 ensures. The printing pulse trigger 18 works together with a hinge bracket t60, which has a Cam 155 carries which are overrun by the feeler roller of the pressure pulse trigger 18 can. The hinge bracket 160 is mounted on a stationary holder 24 at 161. Between Holder 24 and hinge bracket 160 is a compression spring 23, which the mentioned Components pushes apart. This moving apart of the components 24 and 160 is limited by an abutment 156 of the hinge bracket 160. The hinge bracket 160 is stationary Via a bearing eye 162 with an actuating rod 146 in connection, which translates can move and as Fig.S shows, on the free end of a two-armed pivot lever 25 acts, which carries a ball head 163 at its free end, which is in the forked The end of the pawl 29 engages. The aforementioned spring 23 ensures that the actuating rod 146 is repeatedly moved back into a waiting position, which it only briefly leaves when the trigger 18 overruns the cam 155 of the hinge bracket 160. the between a fixed component and the pivot lever 25 arranged spring 164 provides that the free end of the pivot lever 25 on the end face of the actuating rod 146 remains in contact when the pawl is advanced and relaxation the compression spring 35 prevents.

After the transmission of a pressure pulse by means of the pressure pulse trigger 18 is also the pawl 29 raised and can then then on the Support the spring abutment 38 until the spring 35 is tensioned again. In the end, it should be noted that the pawl 29 held taut Spring 35 comes to relaxation each time and then displace the cam 4 slightly can when the pressure pulse trigger 18 in the bottom dead center position of the crank pin 120 acts on the cam 155.

In other words, this means that the pressure pulse trigger 18 determines when energy is removed from the sprocket 2 by means of the force-absorbing cam 32 shall be.

Another locking and unlocking relates to the pivot arm 27, the is also actuated as a function of the position of the rotor 20. In this Trap is also located on the hub of the shaft 17 of the rotor 20, a swivel arm lock 16. This swivel arm release control 16 is around 1800 compared to the pressure pulse trigger 18 arranged offset and also provided with a feeler roller at its free end, which, however, are not employed radially, but tangentially with respect to the rotor shaft 17 is and cooperates with a small plate 43 (see. Fig. 10, 11 and 13). As soon the swivel arm locker 16 rotates with the rotor shaft 17 and the plate 43 acted upon, the control rod 12 connected to the plate 43 rotates, which rests in the stationary bearing 157. Beyond the camp remote from plate 43 157, the control rod 12 is cross-shaped (FIG. 11). The free end of the Control rod 12 engages in a stationary bushing 152, in which a thrust bearing is located. This thrust bearing is necessary because of the axial stroke the control rod 12 the full reaction force of the two working springs 14, 14 'momentarily must take up. There is a roller 150 on one cross arm 165 and on the other Cross arm 166 an abutment 167 for two helical tension springs 151, which are for the waiting position define a neutral position of the control rod 12.

The swivel arm release described so far works during operation as follows: When the pivot arm 27 with respect to the F i g. 1 pushed to the right as far as possible and the springs 14, 14 'has been tensioned, the cross arm provided with roller 150 rolls 165 behind the plate 15 attached to the pivot arm 27 and thereby locks the Swivel arm 27.

This locking takes place against the force of the springs 151. Here the plate 43 connected to the control rod 12 is in the waiting position brought; it then lies approximately horizontally. As soon as the connecting rod 22 is the upper When dead center is reached, the pressure plate 43 is released by means of the feeler roller of the unlocker 16 depresses. As the cross arm roller 150, as it is connected to the plate 43. moves to the side while tensioning the opposing helical tension spring, the pivot arm 27 is released again.

The locking and unlocking process described above takes place only once in each case with a full revolution of the rotor 20.

The pressure pulse trigger works at the bottom dead center, around the swivel arm and the swivel arm release control at top dead center to move the swivel arm to free again for the backward movement. The pressure pulse trigger also works only once per full rotation of the rotor shaft.

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Claims (9)

Claims: 1. Device for equalizing and transferring of rotational energy between an irregularly driven input shaft and a more evenly rotating output shaft stabilized with a flywheel, d a d u r c h g e k e n n -z e i c h n e t that the input shaft (102) is a sprocket (2) carries that the output shaft (17) is connected to a crank mechanism (21, 120, 22) is that an energy pulse transmitting connection between the input shaft (102) and output shaft (17) from a parallel axis next to the circumference of the Sprossenrades (2) arranged camshaft (6), one carried by the camshaft (6), energy-absorbing, from a waiting position between the rungs (1) of the sprocket wheel (2) movable energy-absorbing cam arm (32), a tappet that can be driven by the camshaft (6) (11) with a spring arrangement connecting the plunger (11) to the connecting rod (22) (14) consists, and that the position of the crank mechanism (21, 120, 22) detecting trigger (18) is present, which has a control (25, 29, 31, 35, 38, 108) for the intervention of the cam arm (32) between the rungs (1) of the sprocket wheel (2) and thus for a rotation of the camshaft (6), for the pulsed loading of the tappet (11), for tensioning the spring arrangement (14) and supporting the movement of the connecting rod (22) ensures. 2. Apparatus according to claim 1, characterized in that the application of the tappet (11) through the camshaft (6) by means of a further cam arm (5) takes place, which is also firmly connected to the camshaft (6). 3. Apparatus according to claim 1 and 2, characterized in that the engagement of the energy-consuming cam arm (32) by means of a further cam arm (4), which is also firmly connected to the camshaft (6). 4. Apparatus according to claim 1 to 3, characterized in that the cam arms parts of rotationally symmetrical design, alternately for engagement coming double cams (32, 4, 5) are, which increase each energy pulse by 1800 turn. 5. Apparatus according to claim 1 to 4, characterized in that the output shaft (17) carrying the flywheel (20) itself is designed as a crankshaft and is connected to a connecting rod (22) via a crank arm (21) 6. Device according to claims 1 to 5, characterized in that the one activated by the plunger (11) Spring arrangement contains two storage springs (14, 14 ') controlled by the circulation of the Crankshaft (17) one after the other non-positively connected to the connecting rod (22) in this way be that one of the springs (14) between the dead centers of the crank pressing and another of the springs (14 ') has a pulling effect. 7. Apparatus according to claim 6, characterized in that. that of the camshaft (6) actuated tappet (11) acts on a Schwenlcann (27) which acts directly on the connecting rod (22) via a crste compression spring (14) and at the same time a second stationary supported second compression spring (14 ') is tensioned. 8. Apparatus according to claim 7, characterized in that the second Compression spring (14 ') depending on the position of the crank mechanism (21, 120, 22) their maximum tension held locked by the swivel arm (27) and only is then released when the connecting rod movement after the dead center has been exceeded reversed. 9. Apparatus according to claim 1 to 8, characterized in that to switch them off on the control linkage (31) of the cam arrangement (4) one manually operable locking rod (140) is provided. The invention relates to a device for equalizing and Transferring rotational energy between an irregularly driven input shaft and a smoother rotating flywheel stabilized output shaft. Because of the running out of natural energy, in particular of fossil fuels, more and more attempts are made to find more naturally occurring ones To utilize energies in a profitable way. A beneficial recovery almost sets in always presupposes that the energies occurring in nature are in some way equalized will. In practice, only one can be uniform, i.e. H. running at constant speed Shaft drive a machine or a generator. The object of the present invention is to provide a new one and improved device for equalizing and transferring rotational energy, which works with relatively low losses and has a purely mechanical structure, so that the device can be operated easily and without external energy and also can be serviced and repaired by mechanics without special knowledge.