WO1996027083A1

WO1996027083A1 - Energy accumulator

Info

Publication number: WO1996027083A1
Application number: PCT/EP1996/000842
Authority: WO
Inventors: Iradj Hessabi
Original assignee: Iradj Hessabi
Priority date: 1995-03-02
Filing date: 1996-03-01
Publication date: 1996-09-06
Also published as: AU4943996A

Abstract

A device for accumulating energy, in particular for vehicle driving systems, has at least one coil spring (10) arranged in a guide cylinder (1) and supported at one end against the guide cylinder (1). The coil spring (10) co-operates with an output gear (22, 26, 27) in order to transmit a rotary movement and has at its other end an insert element (11). In order to develop such a device so that it forms an environmentally-friendly, economic driving system that may be used in vehicle construction either alone without internal combustion or combined with internal combustion engines, the inner wall of the guide cylinder (1) has thread-shaped grooves (8) and the insert element (11) has at least two radially projecting fingers (18) that engage the grooves (8) of the guide cylinders and are rotated at least when the spring (10) is released, converting the linear movement of the spring (10) compressed by energy supplied thereto and stored in the form of elastic deformation into a rotary movement when the spring is released. This rotary movement can then be transmitted by the output and the output gear to the drive side as driving energy.

Description

Energy storage

The invention relates to a device for storing energy, in particular for use in drives, such as a vehicle drive with at least one helical spring arranged in a guide cylinder as an energy store and an output gear, the helical spring being supported at one end against the guide cylinder and on it the other end has a spring insert, the spring insert cooperating with an output gear.

The known vehicles are usually driven by internal combustion or electric motors. In internal combustion engines, the combustion process in the cylinders takes place separately in each vehicle. It must therefore be filled with fuel, usually with gasoline, diesel or gas and similar mixtures. All internal combustion engines release innumerable pollutants into the environment that overwhelm the natural self-cleaning power and are not or only partially broken down. They also cause relatively high noise levels and are prone to repairs. More common

ORIGINAL DOCUMENTS These vehicles are supplied with the fuel in petrol stations, which are therefore equipped with several large tank systems, which also pose a hazard from the exhaust gases and from a risk of explosion; The same also applies to vehicles which, fueled with fuel, take part in road traffic. Significant amounts of such fuels are burned daily, so that air pollution and health risks increase. The resulting damage and contamination are problematic; the decontamination of contaminated air, soil and groundwater is very complex and often cannot be fully managed.

It has also already been proposed to couple internal combustion engines to an energy store in order to obtain a travel drive without internal combustion, for example in cities. For this purpose, flywheels were used which, outside of the inner-city driving range, brought high speeds and were to replace the combustion engine on (relatively) short distances.

Electrically powered vehicles require electrical energy, which is also primarily generated by burning fuels; however, this generation takes place centrally, so that flue gas cleaning can be carried out effectively and the emission of pollutants to the environment is reduced. They are also quieter than internal combustion engines and hardly require repairs. However, they are less powerful and require heavy and voluminous accumulators that have to be transported. High energy loss and insufficient power are obstacles to using such drive motors in the vehicle sector. Other electric vehicle drives are electrically powered electric motors via a direct connection, for example electric locomotives powered by overhead lines, tram railcars or overhead line buses; these motors are more powerful, but their energy loss is also not negligible due to the distance-dependent line losses, especially since the system is expensive to invest because of the overhead lines and is always tied to a return line, for example via rails or a second overhead line. DE-GM 8816417 describes a mechanical energy store with a coil spring in a guide cylinder, which can be tensioned by pressure or tension. The tensioned spring expands linearly in the guide cylinder, this linear expansion being diverted via a multi-stage gear, possibly with a backstop. It is also possible to combine a plurality of single-cylinder stores into a multiple store, which operate on the same output gear. In order to obtain a rotational movement from this linear movement, very high gear ratios are required, in particular because of the (relatively) short storage path, in order to obtain a rotational movement that is sufficient for drive purposes, a considerable part of which remains unused as a gear loss. Furthermore, DE-PS 844 096 describes an energy store for a spring motor, which is provided with a helically wound spring, which, however, is neither compressed nor pulled apart for energy storage, but rather is used to store energy by rotating movement " is wound up ", so that the winding diameter is reduced, which increases again when" relaxing "while releasing energy. Due to its design, this arrangement provides a priori a rotational movement in the output; a spring insert for reshaping a linear movement is not required here.

It follows from the object of the invention to propose a generic device which, in a simple construction with a rotational movement, carries out energy stored in a helical spring in an environmentally friendly and economical manner which can also be used as a drive alone or in conjunction with internal combustion engines without the use of internal combustion can be used in vehicle construction.

The solution to the problem is that an energy supplied to an energy store is used as the drive energy, the energy store having at least one guide cylinder in which a helical spring is arranged. This is supported at one end against one of the ends of the guide cylinder and has at its other end a spring insert which is provided with at least two radially projecting radial fingers. These radial fingers engage in thread grooves at least when the coil spring is relaxed a, which are provided on the inner wall of the guide cylinder and are guided in a rotational movement. By means of these radial fingers, the inertial movement when the helical spring is released, which is tensioned by energy stored in the form of elastic deformation, is converted into a rotating movement, which can be transmitted as drive energy to the output. The spring insert provided at the free end of the coil spring is designed in such a way that an advantageously hydraulically actuated tool can engage it, which tensions the coil spring by stretching or compressing it. The work stored by compressing or stretching the helical spring tries to lengthen the spring - in the case of compression - or to shorten it - in the case of expansion. For energy storage in small drives, such as a clock or toy drive, it is known to use spiral springs which are able to save work and, if required, to release this directly as rotational work; However, due to the conditions of a spiral spring, only a small amount of work can be stored in them, sufficient for such small drives.

It is advantageous here when the thread grooves form a multi-thread on the inner wall of the guide cylinder, cases with a number of independent ^threads', which corresponds to the number of radial finger or an integral fraction thereof; For example, two tracks for four radial fingers, arranged in two pairs offset by 90 °, or three tracks for six radial fingers, which are arranged opposite each other in three pairs offset by 60 °, or three Paths for nine radial fingers, three each offset by 120 ° in a group, the groups are offset by 40 °. This multiple thread allows the radial fingers to be arranged in a plane perpendicular to the axis of the helical spring (or several planes provided at a short distance from one another) with rotationally symmetrical distributions. Force moments that must occur when the radial fingers are arranged in a plane oblique to the axis are at least largely prevented.

In an advantageous embodiment, the guide cylinder is rotatable and the spring insert is rotatable relative to the frame. securely mounted, the guide cylinder being operatively connected to the driven gear. In an alternative embodiment, the spring insert is rotatable and the guide cylinder is fixed to the frame, the spring insert being operatively connected to the driven gear. Both embodiments convert the linear movement with great force into a rotating one in that the radial fingers are guided in the thread grooves of the guide cylinder during the axial displacement associated with the relaxation. While the guide cylinder itself rotates in the first case, the spring insert rotates in the second case; in both cases the rotary movement is transmitted to the output gear and is available there for drives.

The radial fingers are provided at their ends with approximately form-fitting engages in the grooves, which are advantageously designed as roller bodies, in particular as balls, which - for example lying on an elastic cushion - are radially displaceable. In another embodiment, the radial fingers are designed to be pivotable with respect to the radius. When tensioning occurs, free-wheel-like conditions arise, the molded bodies are free from the positive guidance in the grooves. During relaxation, there is frictional engagement and the molded bodies, which are positively guided in the thread grooves, execute the rotational movement. The shaped bodies designed as balls can in turn also be mounted in a ball bed to further reduce friction, which reduces friction-related losses and improves the efficiency. When stored on an elastic cushion, its elastic restoring forces ensure that the rolling elements come into positive contact with the steep flanks of the thread grooves when the force flow is reversed. When the radial dial fingers are articulated, it is advantageous if the articulation joints cooperate with return springs, so that here too the force flow which is released when the coil spring is tensioned is restored when the force flow is reversed. Both the radial displacement and the pivoting relative to the radius serve to ensure that the engagement of the shaped body and the thread groove is released when the coil spring is tensioned and is produced when the coil is relaxed. The spring insert provided at the free end of the helical spring is advantageously formed by a shaft which is inserted centrally into the helical spring, the shaft end of which is assigned to this end of the helical spring and is provided with a support plate with an attachment for insertion into the helix of the helical spring. and with an end plate that interacts with the radial fingers. As far as the guide cylinder is arranged fixed to the frame, the support plate is rotatably arranged on the shaft that is operatively connected to the drive gear; Because of the slow movement, no special radial bearing is required. To reduce the friction, it is advantageous if friction-reducing means are provided between the end plate and the support plate, for example in the form of intermediate rings, in particular made of low-friction materials, such as, for example, polytetrafluoroethylene or the like, or axial rolling element bearings, for example ball or Cylinder bearings.

The coil spring of the energy store is tensioned by means of a tension (or compression) rod with which the shaft can be brought into operative connection and which is operated by a conventional hydraulic pressure or tension force generator. To tension a helical spring that is subjected to pressure, the shaft is pressed into the guide cylinder by means of the hydraulically actuated push rod, the support plate driving and tensioning the helical spring. During the pressing in, the rolling elements, which are each arranged on a radial finger, are lifted out of the thread grooves; after tensioning the coil spring they snap back into the thread grooves. As a result of this design, the energy store is tensioned without rotation; the relaxation following the tensioning can only take place with the rolling of the rolling elements in the thread grooves.

An advantageous embodiment for transferring the rotational movement from the energy store to the driven gear is given in that the rotatable part, either the guide cylinder or the spring insert or the shaft connected to it and protruding from the guide cylinder, has a ring gear has that cooperates with a gear that forms the input side of the drive gear. If the rotational movement decreases on the guide cylinder, it suffices if the end face is toothed, since the guide cylinder undergoes no axial displacement. If, however, the rotational movement is removed from the ring, it is advantageous if it is extended out of the guide cylinder and toothed on its outside, this outside toothing cooperating with the toothed wheel designed as a pinion, the length of which corresponds to the stroke of the helical spring.

Gears from other energy stores can also be provided on this gear or the pinion, provided that they do not interfere with one another in their axial movement.

Another, likewise advantageous embodiment, to set the tensile or compressive force of a helical spring into a rotational movement can take place in that the helical compression spring is supported at one end against one of the ends of the guide cylinder and at its other end has a spring insert, which with at least two radially projecting arms is provided. In the case of a helical tension spring, it is attached at one end to one of the ends of the guide cylinder. The guide cylinder is provided with at least two opposite elongated openings. The lateral openings are designed as guide slots for the radially protruding fingers attached to the free end of the spring and are axially parallel, so that they can guide the radially protruding finders in an axially parallel way when the spring is released.

The ends of the radially arranged arms, which are led outwards through the lateral cylinder openings, are each connected to chain drives or toothed belt-like drive trains that interact positively with the driven wheel. By means of these radial arms, when the spring is released, the energy stored in the form of elastic deformation of the tensioned coil springs is transmitted via a linear movement to the drive trains, which are carried along by the arms during their axis-parallel movement.

Because the drive trains are guided as endless drives over rollers, the axial linear movement becomes a rotating movement implemented, which can be transferred as drive energy to the output. The spring insert provided at the free end of the coil spring is designed in such a way that an advantageously hydraulically actuated tool can engage it, which tensions the coil spring by stretching or compressing it.

In an advantageous embodiment, the guide cylinder is rotatable and the spring insert is secured against rotation relative to the frame, the guide cylinder being operatively connected to the drive gear. In an alternative embodiment, the spring insert is rotatable and the guide cylinder is mounted fixed to the frame, the spring insert being operatively connected to the drive gear. Both versions convert the linear movement that occurs with great force into a rotating one in that the radially attached arms are connected to a corresponding drive train during the axial displacement in the guide cylinder associated with the relaxation.

The spring insert provided at the free end of the helical spring is advantageous, formed by a shaft which is introduced centrally into the helical spring and the end of which is assigned to this helical spring end has a support plate with a shoulder for the helix of the helical spring and one End plate that interacts with the radially arranged arms. As far as the guide cylinder is fixed to the frame, the support plate is rotatably arranged on the shaft that is operatively connected to the drive gear; Because of the slow movement, a special radial bearing is required.

The coil spring of the energy store is tensioned by means of a tension (or compression) rod with which the shaft can be brought into operative connection and which is operated by a conventional hydraulic pressure or tension force generator. To tension a helical spring that is subjected to pressure, the shaft is pressed into the guide cylinder by means of the hydraulically actuated push rod, the support plate driving and tensioning the helical spring.

The radially arranged arms, each connected to the drive cables are bound, bring two rotatable rollers into rotation and can transmit their movement to at least one shaft by means of gear wheels or the pinion. Several roles can be connected to this shaft. In all the embodiments described, be it with guide cylinders with thread-shaped guide aisles or with opening slots arranged on the side, the radial course of the coil springs is converted into rotational movements during relaxation.

In both cases the circumference of the driving gearwheel cooperating with the helical spring is large compared to that of the driven gearwheel, so that the (relatively) low speed of the driving gearwheel is translated, so that the drive gear with a (relatively) is operated at high speed.

This drive gear then sets the speed to the value corresponding to the requirements. In this case, a flywheel can also be provided, in particular on the last transmission shaft running at the highest speed, which is capable of bridging drive irregularities.

In a preferred embodiment, a continuously variable transmission is provided as the output transmission; for this purpose, the output shaft of one or more energy storage devices, which is optionally provided with a flywheel, is provided with a friction wheel which interacts with a corresponding friction cone arranged in a parallel axis, the surfaces of at least one wheel being an adhesive one; this adhesive surface is advantageously achieved by rubber coating. The friction cone is designed such that it is pressed onto the friction wheel with a circumferential area assigned to a specific radius in order to absorb its rotational movement, the friction cone being arranged in such a way that it can be displaced parallel to the shaft of the friction wheel. As a result, the rotational speed and standstill of the friction cone are dependent on its position. In order to compensate for the axial displacement, the friction cone is provided with a shaft, at the end of which a gear wheel is arranged. which meshes with a further gearwheel, one of these gearwheels being designed such that it is elongated in accordance with the stroke of the friction cone adjustment so that it is attached to the shaft of the friction cone. arranged gear is constantly engaged with the last gear in the case of axially parallel displacement. The rotation of this last gear is, as usual, transmitted to the vehicle wheel or the drive axle.

It is advantageous if at least one axial locking groove is provided on the surface of the shaft and that at least one locking bolt is pivotably arranged on the outer wall of the guide cylinder in such a way that the axial relaxation movement of the tensioned coil spring is stopped with it; the locking bolt is inserted into the groove. This locking bar can be inserted into the groove by pulling or pushing. If several energy stores are arranged next to one another, the locking bars of the individual energy stores can be inserted into the groove by pressure, starting from the gearwheel arranged on the shaft, the locking bar of the following energy store being lifted out of its groove. A further energy store can thus relax with the release of drive energy, after the drive energy stored in the first energy store is used up and relaxed. The gears on the shafts are provided with a freewheel which allows the gearwheel which is in engagement with the pinion to rotate when the power flows from the pinion to the gearwheel, the shaft itself resting, while when the power flows from the gearwheel to the pinion this lock is released and the rotational movement of the shaft caused by the relaxation is transmitted to the pinion.

The tensioning device for the energy store is advantageously a hydraulic pressing device, the tool of which can be adjusted in the respective vehicle height. The hydraulic cylinder, with which the coil spring of the energy store is to be tensioned, is provided with at least two gripping heads which guide the shaft ends provided with receptacles, lock them, and can be removed after tensioning the coil spring and the subsequent relief. Such hydraulic devices can be easily set up at petrol stations so that vehicles there can not only hold liquid (or gaseous) fuels, but also their built-in energy stores can be tensioned with coil springs. Several such energy stores can be installed in a vehicle. For example, each energy storage device can be preloaded with a force of at least ten tons (100 kN). The effective length of the cylinder inner wall can be provided with thread grooves for at least 1200 revolutions. At one revolution per second, the rolling elements run for 20 minutes. According to this example, a vehicle with 3 such energy stores can be kept in operation continuously for 1 hour, and one with 15 such energy stores for five hours. If this energy store is combined with an internal combustion engine as a hybrid drive, it is also possible to drive through areas in which vehicles with internal combustion engines are not allowed to run.

The essence of the invention is explained in more detail with reference to the exemplary embodiments illustrated in FIGS. 1 to 6; show

Fig. 01: detail energy storage with coil spring;

Fig. 02: Detail of spring insert with shaft, Fig. 2a: Spring insert with print head, Fig. 2b: Spring insert with pulling head;

Fig. 03: Energy storage drive with bevel gear, maximum gear ratio;

Fig. 04: Energy storage drive with bevel gear, minimal gear ratio;

Fig. 05: Multiple energy storage for drive purposes;

Fig. 06: Motor vehicle with energy storage;

Fig. 07: Charging a motor vehicle with coil spring energy storage;

Fig. 08: Schematic representation of a motor vehicle with spring drive;

Fig. 09: Detail energy storage with coil spring;

Fig. 10: Spring insert with pulling head.

FIG. 1 shows an embodiment of an energy store with two guide cylinders 1 suitable for drive purposes, in each of which a helical spring 10 is arranged concentrically, one end of which is supported against the end face 4 of the guide cylinder 10. The the other end of the helical spring 10 interacts with a spring insert 15 which has a support plate 16 with an attachment 16.1 receiving the end of the helix of the helical spring 10 and an end plate 17 which is rotatable relative to the support plate, with a (not shown and designated) axial roller bearing is provided. In addition to the rotatable end plate 17, radial fingers 18 are provided, which are provided with rolling bodies 18.1 at their outer ends. These rolling elements 18.1 engage in the thread grooves 8 provided in the guide cylinder 1 and are guided there. The radial fingers 18 are articulated to the end plate 17 by means of pivot bearings 18.2 and can thus be pivoted against the radius. As a result, they can "dodge" and become disengaged when the helical spring 10 is tensioned, which is facilitated by the flat flanks of the thread grooves 8, while their steep flanks, which come into effect when the helical spring is relaxed, since the rolling elements 18. 1 form-fit , together with the linkage locked in this direction, enable the force to be applied.

The outer end of the shaft 12, which is guided on a guide 12.1, is provided with a toothed wheel 14 which can be moved along a pinion shaft 5. This Rit∑elwelle 5 transmits the removed rotation to a flywheel 7, with which irregularities in the movement are compensated for, for example by inhibiting points.

In order to be able to relax the energy stores one after the other, the individual drives of the energy stores can be blocked; for this purpose locking lugs 9.1, the locking grooves of the pinion shafts 5 are inserted, the movement of which locks. A (pedal) linkage 9.2 is used to lift the lock, with which the locking lug 9.1 can be lifted out of the locking groove or lowered into it. In order nevertheless to make it possible to move the drive, these output gearwheels 14 are equipped with freewheeling in such a way that a force connection is established when force is applied via the shaft 12, but this force connection is canceled when the force flow is reversed. It goes without saying that it is possible to chain these locking tabs 9.1 within the energy storage groups in order to be able to relax the individual energy stores in a group one after the other, the groups being both parallel can also be connected in series.

The details of the spring insert 15 are shown in FIG. 2, a spring insert 15 with a press head 19.1 being shown in FIG. 2a and a spring insert 15 pulling head 19.2 being shown in FIG. 2b. The helical spring 10 is arranged concentrically in the guide cylinder 1, the end of which rests on the spring insert 15; for this purpose it is provided with a support plate 16 with a shoulder 16.1 receiving the helix of the helical spring, against which the helical spring 10 presses with a force corresponding to its tension. This force is transmitted via the axial bearing 17.1 to the end plate 17 and thus to the radial fingers 18, which engage with their rolling elements 18.1 in the thread grooves 8 of the guide cylinder 1 and which - as a result of the axial movement of the Spring insert 15 - perform a rotating movement following the thread line. The end of the shaft 12 forms a clamping head 19 to which a tool 33 (FIGS. 4, 8) required for tensioning the coil spring 10 can be attached.

This rotating movement is transmitted to the shaft 12. The shaft 12 emerging from the end of the guide cylinder 1, which from the shaft extension 12.1 - s. 1 - is now driving the gear 14 connected to it, which meshes with the pinion 5. With the axial movement of the spring insert 15 with the shaft 12, this gear 14 also moves to the same extent; therefore, this pinion 15 as a toothed shaft is as long as the range of motion of the coil spring 10 requires. The thread grooves 8 are formed such that one flank 9.1 is steep and the other flank 9.2 is kept flat. This asymmetrical design serves to enable clamping without rotation. For this purpose, the rolling elements 18.1 engaging in the thread grooves 8 are radially displaceable or pivotable with respect to the radius. When the helical spring 10 is tensioned by external forces, the radial fingers 18 can deflect in order to cancel a non-positive connection, this evasion by the flat flanks 9.2 of the thread grooves 8 is favored. In the opposite direction, the rolling elements 18.1 bear approximately positively on the steep flanks 9.1 of the thread grooves 8 under the force exerted by the helical spring 10, so that frictional engagement in this direction of movement exists and the axial expansion of the coil spring 10 due to the spring force can be implemented in a rotational movement. The radial displacement is expediently carried out by means of an elastic cushion; for pivoting pivot bearings 18.2 are provided with which the radial fingers 18 are articulated on the end plate.

FIGS. 3 and 4 show the drive with the energy store according to FIG. 1 with a drive gear 20. The rotary movement emitted by the shaft 12 is transmitted to the flywheel 7 and from there via a shaft 21 to a friction wheel 22 which is connected to a Friction cone 25 interacts, one or both of which are provided with appropriate adhesive coatings to improve the friction or are made of appropriate adhesive materials. Via the bevel gear holder 23, the position of the friction cone relative to the friction wheel can be adjusted by means of an adjusting mechanism 24, and thus the transmission ratio and thus the output speed can be changed. This adjustment mechanism 24 is operated by a pedal pull 24.1; the reset takes place via the return spring 24.2. 3, the transmission ratio is set to the maximum value, and in FIG. 4 to the minimum value; This results in speeds between 3 and 30 rpm in the example. If the friction cone 25 is shifted further from the minimal gear ratio (FIG. 4) in the direction of the lower gear ratio, it disengages and the force path is interrupted.

5 shows the use of 4 energy stores in two pairs, the energy stores with their output gearwheels 14 connected to the shafts 12 (only the reference numbers for an energy store are entered), arranged rotationally symmetrically around the respective pinion shafts 5 are, the flywheels 7 are provided with sprockets, which mesh with the transmission gear 21.1 of the gear shaft 21 and thus establish the force path connection between two groups of energy storage. It goes without saying that further energy stores can be added which act on the drive one after the other, wherein a parallel connection of groups of energy stores is also conceivable.

FIG. 6 shows an application of the energy store as a drive for a wheel 28 of a motor vehicle in a perspective diagram. Of the Only one of the guide cylinders 1 is still tensioned in the illustration; its gearwheel 14 connected to the shaft 12 is close to its end plate; the other guide cylinders 1 are relaxed, their shafts 12 are extended, their gears 14 are close to the transmission 20. The shaft 21 of the transmission is connected to the friction wheel 22, from which the drive of the generator 29 is also branched off. The friction cone 26, which is driven by the friction wheel 22, drives the drive roller 27 and thus the wheel 28 in the manner described above via the toothed plate 26.

FIGS. 7 and 8 show an application example in connection with a motor vehicle 30. The (relatively) long guide cylinders 1 of the energy stores with the transmission 20 are arranged in the longitudinal direction of the vehicle. This allows a long stroke of the helical springs sufficient for a sufficient operating time, especially since the length of the pinion shaft 5 corresponding to the stroke distance has to be taken into account in the length of the entire device. The tensioning of the coil spring and thus the charging of the energy store is expediently carried out from the rear of the vehicle 31, the (indicated) tensioning tools 33 being inserted through the holes 2.1 in the bottom 2 of the guide cylinder 1 (FIGS. 1, 2) and attached to the tensioning head 12.2 Wave 12 are coupled. A height-adjustable hydraulic system 32 presses (or pulls) the tool 33 and thus tensions the coil spring 10 in the interior of the guide cylinder 1.

It goes without saying that the vehicle 30 is supported during tensioning, especially since the brakes of the vehicle would hardly withstand these forces; this support takes place via the end plates 2 (FIGS. 2a, 2b) of the guide cylinder 1, so that the motor vehicle is relieved.

FIGS. 9 and 10 show the second embodiment, in which circumferential endless drives (42) are provided as drive trains with toothed belts or chains. These endless drives (42) are attached to the outer ends of the radial arms (41) which are brought up through the slots (1.1) from the guide cylinder (1).

The helical spring (10) is designed here as a tension spring, on the free end of which a cap (40) which receives the spring insert forms, is placed, and which is provided with the radially projecting arms (41) which engage through these axially parallel slots (1.1). A tower of the endless drive (42) is attached to the outside of this radially projecting arm (41) and, guided over deflection rollers (43), runs in a loop over the driven rollers (44). While the deflection rollers (43) mounted on an axle (43.1) run freely in both directions of rotation, the output rollers (44) are mounted on the output shaft (45) in such a way that they are locked in the direction of rotation of the output while they are locked in opposite direction of rotation run freely.

Unless a direct drive is provided, the output shaft (45) acts on the transmission which takes over the drive energy, whereas in the case of countershaft gears (46) bring the speed into a range suitable for the input of the drive. These countershaft gears (46) are set up so that they also force-synchronize corresponding output shafts (44).

It goes without saying that this forced synchronization can also be effected with separate meshing gears (47) arranged on the output shafts (45). To tension the tension spring (10), the cap (40) of the spring insert is provided with a towing eye (40.1) to which the tensioning means causing the tensioning is applied, that through the opening (2.1) in the bottom (2) of the Guide cylinder (1) can be inserted. One of the two output shafts (45) is provided as the output and is brought up as the output shaft (48). In order to have certain energy reserves available, flywheels (49) are arranged on this output shaft (48), which can be engaged and disengaged, so that unevenness in the energy output caused by the type of relaxation of springs under different tension are compensated for can.

In order to be able to take the energy stored in the individual guide cylinders one after the other in the case of a plurality of guide cylinders arranged in parallel in the manner of a “series connection”, a locking device is provided, which is formed by two release levers (52, 53) connected via a tension member (51) is. When the helical spring (10) of a guide cylinder (1) is tensioned, the lower release lever is (53) not active, the freewheel of the assigned driven gear (44) is switched to freewheeling in both directions. After the helical spring (10) assigned by the previously arranged guide cylinder has been released, its upper release lever becomes active, which now activates the lower release lever (53) of the following guide cylinder (10), so that its associated freewheeling of the driven wheel (44) is now blocked in the drive direction is and can transmit power to the output shaft (45). Since there is now no force input via the driven wheel of the preceding guide cylinder, the one-way freewheels with which the individual driven wheels (44) are arranged on the driven shaft (45) are sufficient to allow the endless drive assigned to the respective driven wheel to run along. Suppress train.

Claims

claims

01. Device for storing energy, in particular for use in drives, such as vehicle drives, with at least one helical spring arranged in a guide cylinder as an energy store and an output gear, the helical spring being supported at one end against the guide cylinder and on has at its other end a spring insert, the spring insert cooperating with an output gear, characterized in that the inner wall of the guide cylinder (1) has thread-like grooves (8) and the spring Insert (11) have at least two radially protruding radial fingers (18) which, at least while the helical spring (10) is being released, are guided in rotational movement so as to engage in the grooves (8) of the guide cylinder, as a result of which the linear movement of the guide fingers , in the form of elastic deformation stored energy tensioned coil spring (10) converted into a rotating movement when relaxed is, which can be transferred as drive energy to the output via the output and the output gear.

02. Apparatus according to claim 1, characterized in that the thread-like grooves (8) on the inner wall of the guide cylinder (1) form a multiple thread, the number of mutually independent gears corresponding to the number of rolling elements or an integer fraction thereof.

03. Apparatus according to claim 1 or 2, characterized in that the cross section of the thread-like grooves (8) is asymmetrical, such that their flanks (9.1, 9.2) in the direction of "tensioning" of the coil spring (10) run flat than in the "relax" direction, the radial fingers (18) engaging in the grooves (8) resting in a force-fitting manner on the corresponding flank in the relaxation direction.

04. Apparatus according to claim 1, 2 or 3, characterized gekennzeich¬ net that the guide cylinder (1) rotatable and the helical spring (10) and with its free end cooperating spring insert (11) are fixed to the frame, the guide cylinder (1) provided with a ring gear being in operative connection with the drive gear (20).

05. Apparatus according to claim 1, 2 or 3, characterized gekennzeich¬ net that the spring insert (11) cooperating with the free end of the coil spring (11) is rotatable and guide cylinder (1) and coil spring (10) are fixed to the frame The spring insert (11) is operatively connected to the drive gear (20) via a shaft (12) passing through the helical spring (10) and coming out of the guide cylinder (1) and provided with a gear (14) .

06. Apparatus according to claim 5, characterized in that the spring insert (11) has a support plate (16) which is supported against the free end of the helical spring (10) and is rotatably mounted on the shaft (12) and which preferably has one in the Helical insert (16.1) is provided, the shaft (12) with the radially projecting the radial fingers (18) cooperating with the grooves (8) is provided.

07. Apparatus according to claim 6, characterized in that the finger-side end of the shaft (12) has an end disc (17) connected to it and cooperating with the radial fingers (18).

08. Apparatus according to claim 7, characterized in that between the support plate (16) and the end plate (17) friction-reducing means are provided, which are preferably designed as a sliding disc or axial roller bearing (17.1).

09. Apparatus according to claim 7 or 8, characterized in that the radial fingers (18) or at least their rolling elements (18.1) provided at their outer ends are radially displaceable, such that when the helical spring (10) is tensioned, the engagement the rolling element (18.1) is lifted into the thread-like grooves (8) and is produced when they are relaxed.

10. Apparatus according to claim 7 or 8, characterized in that the radial fingers (18) are articulated with respect to the radius so that they can be pivoted to the end plate (17), the joints (18.2) preferably being provided with springs which press the radial fingers (18) back into their original position in such a way that when the helical spring (10) is tensioned, the engagement of the rolling elements (18.1) in the thread-like grooves (8) is released and is released when they are relaxed.

11. The device according to claim 9 or 10, characterized in that the end of the radial finger (18) which cooperates with the grooves (8) can be inserted with substantially form-fitting rolling elements, preferably in the form of a ball, in the groove (8) (18) is provided.

12. The apparatus according to claim 11, characterized in that the ball of the rolling body (18.1) is gela¬ gert in a ball bed.

13. Device according to one of claims 6 to 12, characterized ge indicates that the shaft (11) is guided through the end plate (17) and its free end is designed as a clamping head (19) interacting with a clamping tool.

14. The apparatus according to claim 13, characterized in that the clamping head is designed as a print head (19.1).

15. The apparatus according to claim 13, characterized in that the clamping head is designed as a pulling head (19.2).

16. The device according to one of claims 6 to 15, characterized ge indicates that the radial finder (18) are arranged rotationally symmetrically distributed.

17. The device according to one of claims 1 to 16, characterized ge indicates that to decrease the rotational movement of the spring insert (11) a gear (14) is provided which meshes with a pinion (5), the length of which is at least the stroke corresponds to the coil spring (10), the drive energy taken from the energy store on the pinion (5) being removable.

18. The apparatus according to claim 17, characterized in that at least two energy stores with guide cylinder (1) and spring insert (11) are provided, the Zahnrit¬ zel (5) being arranged centrally between these energy stores.

19. The apparatus of claim 17 or 18, characterized gekennzeich¬ net that locking means (9) are provided with which the energy consumption of each of the energy storage can be locked and released, the abortive gears (14) with free are provided in such a way that when the force flows from the shaft (12) to the gear wheel (14) there is a force fit, while a reversal of the force flow eliminates the force fit.

20. The apparatus according to claim 19, characterized in that a locking groove in the shaft and in the insertable locking lugs (9.1) are provided as locking means, which are pivotable by means of a lever device (9.2), preferably a Winkel¬ lever.

21. The apparatus according to claim 20, characterized in that the angle levers (9.2) of a plurality of energy stores are chained together in such a way that a gradual decrease in energy is possible.

22. Device according to one of claims 1 to 21, characterized in that the free end of the helical spring (10) has a spring insert (40) with at least two radially projecting as a means for implementing the linear movement in rotational movement Fingers (41) is provided, and that for each of the fingers a driven idler pulley (43) and a driven pulley (44) arranged on the driven axis (45), which is locked in the driven direction and freely running in the opposite direction, are guided Endless drive (42) with toothed belt, chain or the like. is provided.

23. The device according to claim 22, characterized in that the radially projecting fingers (41) through the axially parallel slots (1.1) provided in the wall of the guide cylinder (1) are guided to the outside, and the endless drive (42) outside the guide cylinder ( 1) are arranged.

24. The device according to claim 22 or 23, characterized gekennzeich¬ net that with a plurality of radially projecting fingers (41) for each finger (41) an output shaft (45) is provided, which at one end with synchronization means, in particular with meshing synchronization gears (47) are provided.

25. Device according to one of claims 22 to 24, characterized ge indicates that at least two energy stores with Füh¬ approximately cylinder (1), coil spring (10) and spring insert (40) are provided, the guide cylinder (1) in series are arranged in such a way that the endless drives (42) corresponding to the output shafts (45) are aligned with the respective output shaft.

26. The apparatus of claim 24 or 25, characterized gekennzeich¬ net that locking means (51, 52, 53) are provided with which the energy consumption of each of the energy storage can be locked and released, the driven wheels (44) with freewheels such are provided that in the case of power flow from the endless drive (42) to the gearwheel (44) there is force closure, while a reversal of the force flow cancels the force closure.

27. The apparatus according to claim 26, characterized in that the locking means cooperate at least with the freewheels of the driven wheels (44), preferably releasing the energy output from one of the guide cylinders (1), its helical spring (10) being relaxed, to the following the guide cylinder (10), the coil spring of which is still under tension, is passed on.

28. Device according to one of claims 1 to 27, characterized ge indicates that the drive gear (20) is a continuously variable bevel gear with a friction wheel (21) and a friction cone (22), the drive of the bevel gear adjustment ( 23) can preferably be carried out by the accelerator pedal (24) of the vehicle (30) driven by an energy store provided with helical springs.