CH711603A2

CH711603A2 - Emissionless drive by gravity.

Info

Publication number: CH711603A2
Application number: CH01431/15A
Authority: CH
Inventors: Fürst Christian
Original assignee: Fürst Christian
Priority date: 2015-10-02
Filing date: 2015-10-02
Publication date: 2017-04-13
Also published as: WO2017055625A1; EP3356673A1

Abstract

An emission-free drive in a wheel body for driving a shaft is based on two systems for shifting weights inside and outside the wheel body. A first system of drive weights (6) on the wheel body serves to generate a drive force for driving the wheel body by means of a lever action by the radial displacement of these weights. A second system of guide weights (5) in the wheel body serves to carry out the radial displacement of the drive weights (6) of the first system; Wherein the guide weights (5) of the second system are displaced substantially in the circumferential direction of the wheel body by the gravity force. The displacement of the weights of both systems is effected by gravity, Which form a two-armed lever on the wheel body and on the basis of the rotation of the wheel body and thus different positions of the guide weights (5) and different radial positions of the drive weights (6). The guide weights (5) and the drive weights (6) are coordinated by scissor elements (4).

Description

Description: The present invention relates to an emission-free drive in a wheel body for driving a shaft via a hub of the wheel body by utilizing the gravitational force, wherein weights arranged in the wheel body are radially displaced to generate a driving force for driving the wheel body.

[0002] Variously designed drive devices are known from the state of the art which are designed for converting the gravitational force into a rotary movement for a drive. For example, a gravitation water pump and a gravitational motor are known from WO 02/079 648 A1. This is based on a drive unit with a rotating flywheel, which has a plurality of radially extending balancing struts. Weight units are displaceable along the balancing struts. The weight units are also coupled to a guide curve which has a greater radial distance from the wheel center on a side of the flywheel than on the lifting side. The weight units are forcibly guided along the balancing struts and the guide curve, So that they have a greater radial distance from the wheel center on the side of the wheel than on the lifting side. The gravitational force of the weight unit is converted into a lever force at the balancer leg so that the flywheel experiences a driving force. On the lifting side, the weight unit has a smaller radial distance from the wheel center, so that a significantly lower lever force is generated.

In a similar manner, a gravity plant operates for generating electricity by means of weight pressure, as described in DE 4 324 231 A1.

[0003] In the known drive systems using the gravitational force, an unfavorable energy balance often occurs. The reason for this can be excessive friction losses, inadequate lever mechanics, unsuitable weight balances or the like. This results in a poor efficiency of the drive system or even a non-functioning of the whole system.

It is therefore an object of the present invention to overcome these disadvantages and to provide an emission-free drive in a wheel body which positively affects the energy balance, minimizes or avoids losses during the rotation of the wheel body and assists a permanent operation of the emission-free drive guaranteed.

[0005] This object is achieved by the invention by an emission-free drive in a wheel body according to claim 1. Advantageous embodiments and further exemplary embodiments are described in the dependent claims.

The emission-free drive in a wheel body according to the invention is based on two systems for displacing and balancing weights inside and outside the wheel body. A first system of weights on the wheel body serves to generate a driving force for driving the wheel body by means of a lever action of the weights by radial displacement of the weights. A second system of weights in the wheel body serves to carry out the radial displacement of the weights of the first system, wherein the weights of the second system are displaced substantially by the gravity in the circumferential direction of the wheel body. The displacement of the weights of both systems is effected by the gravitational force acting on the weights in different ways on the basis of different positions of the weights at and in the wheel body.

In an emission-free drive with a wheel body for driving a shaft by means of displaceable weights according to the invention, the wheel body has a central at least approximately horizontal hub with a plurality of at least partially radially extending displacement rails and guide rails inserted between two displacement rails Are arranged. For the displacement of guide weights along the guide rails and drive weights radially to the center of the hub, a plurality of weights are provided with scissor-type movable scissors elements on which the weights are supported by which the weights relative to the hub can be displaced. A shearing element at a first end has a guide weight, which is displaceably mounted in a guide rail,

In a rotary movement of the wheel body, the guide weight is displaceable by the gravity from a first position with a first energy level to a second position with a second energy level which is lower than the first energy level along the guide rail. The first position of the guide weight in the wheel body is higher relative to the second position so that the first position has a greater potential energy than the second position and the guide weight due to the gravitational force can dislodge from the first position along the guide rail into the second position. As a result of the displacement of the guide weight along the guide rail, the scissor-like movement of the scissor members of the scissors element and thus the radial displacement of the drive weight occurs. By opening and closing the scissor members during the scissor-like movement of the scissor element, the drive weight is radially displaced in such a way that the drive weight is located in a radially inward position on the upward side of the rotary movement of the wheel body and the drive weight in a radially outward position on the downward side of the rotary movement , As a driving torque is exerted on the wheel body because, according to the lever law, the gravitational force at a drive weight in the outer position induces a greater weight (downward) force than in the internal position. The displacement rail serves as a lever arm on which, on the one hand, the weight force of the drive weight engages and the shearing elements act and, on the other hand, as a force transducer for converting the gravitational force into a drive force.

[0009] In summary, the drive weight is located in a retracted position with a small radius to the hub center during an upward movement; When the lead weight is on the up side in the second, ie the lower, position. On the other hand, the drive weight is located in an extended position with a large radius to the nabal center during a downward movement; When the lead weight is on the down side in the second, ie the lower, position. The two lower positions in the upward and downward movements result from the co-ordinated lateral displacement of the guide weights in the guide rail. It is to be noted that the guide weight during the upward movement of the wheel body absorbs potential energy during and, although in the second, ie the lower position, remains. At the upper apex in the transition from the upward to the downward movement, the guiding weight gives off this potential energy and, from the optics of a horizontal mirroring, also displaces the second, ie the lower, position in the same direction. This results in a system with a two-armed lever in the form of two opposing displacement rails. The lever arm (load arm) of the drive weight on the up side is shorter than the lever arm (force arm) on the down side.

During the rotational movement of the wheel body, the guide weight is lifted upwards from the second position to the first position by the upward movement, and automatically displaces again at the upper apex point during the transition from the upward movement into the downward movement due to the gravitation and the effect of the horizontal reflection The new second position. In essence, the second position of the guide weight is in the upward movement at one end of the guide rail and in the downward movement at the opposite end of the guide rail. The displacement of the guide weight is transformed by the shearing elements into the movement of the drive weight.

[0011] The two systems for weight displacement on the wheel body enable minimal friction losses due to an intrinsic force effect on the basis of gravitation. This has a positive effect on the balance of the emission-free drive and supports a sustainable operation of the emission-free drive. The intrinsic force effect on the overall drive system by means of the guide and drive weights favors the continuity of the drive and thus assists in a more efficient use of energy.

[0012] The shearing element of a wheel body according to the invention has at least two oblong shear members, which are rotatably connected to one another. Preferably, the scissor members are interconnected with each other so that both the first ends and the second ends of the scissor members can perform scissor movement. One of the at least two scissor members is fixed at its first end relative to the guide rail, and the other of the at least two scissor members carries the guide weight at its first end and is movable relative to the guide rail. As a result of the displacement of the guide weight along the guide rail, these ends of the scissor elements are moved toward or away from one another and the scissor element performs a scissor movement. The drive weight can be arranged at the second end of the at least two scissor members. It can be held by both scissor members or even by a scissor member. During a rotational movement of the wheel body, the guide weights remain substantially the same radial distance from the hub center, since they are held in guide rails and moved along these. However, the drive weights can be displaced radially.

At the second end of the at least two scissor members, a further scissor member is movably mounted, wherein the further scissor members are also connected to one another in a scissor-like manner in order to be able to perform a scissor movement. The shearing element is constructed in this way in the manner of a Nuremberg scissors with several pairs of shearing elements. If further scissor members are provided, the drive weight is attached to the second end of the further scissors members. The further scissor members serve to extend the radial path of a drive weight from the inner to the outer position. As a result, the lever effect of the drive weight on the displacement rail can be increased.

[0014] In an advantageous embodiment of the wheel body according to the invention, the displacement rail extends up to the radially outward external position of the drive weight. As a result, the displacement rail can provide a guide for the drive weight and / or in the outward position of the drive weight when the drive weight is extended.

In a further advantageous embodiment of the wheel body, the displacement rail can be provided angled in such a way that it extends at least approximately radially between the hub and the guide rail and is angled off from the guide rail in the direction of rotation of the wheel body. As a result, the displacement rail is lowered in the region for guiding the drive weight on the downward side so that the displacement rail on this side is less steep and the displacement of the drive weight is simplified.

[0016] Preferably, the guide weight and / or the drive weight are installed in a floating manner. For example, if the guide weight is floating in the guide rail, the guide weight is held with some clearance within the guide rail. The play prevents unnecessary friction or tilting of the guide weight.

[0017] In a further advantageous embodiment of the wheel body according to the invention, the guide weight is designed in a cylindrical shape and is mounted only in points in the guide rail. When the guide weight is displaced in the guide rail, this can roll on the narrow surface of the rail and the rolling friction between guide weight and rail is minimized. The same applies to the drive weight. This, too, can be designed in a cylindrical shape and can rest against the displacement rail.

[0018] The geometry of the gravitational wheel is determined by the arrangement of the radial displacement rails and the circumferential guide rails. Preferably, the guide rails form a point-symmetric polygon, particularly an octagon, around the hub. In this case, the guide rails are advantageously straight-line, but can also be slightly curved. The guide rails of the wheel body preferably all have the same length. Thus, the polygon has equiangular segments between the displacement rails. The guide rails are advantageously arranged at the same radial distance from the hub, so that a balanced weight distribution is present between all segments. In principle, however, it would also be conceivable to provide guide rails with different distances from the hub and / or different length,

[0019] For optimum operation of the drive according to the invention, it is important to match the guide weight and the drive weight. In principle, the guide weight is heavier than the drive weight. The guide weight must be heavy enough in relation to the drive weight in order to be able to lift the drive weight by means of a scissor element during its displacement from the first position into the second position in the guide rail so that the lever force which generates the drive weight on the displacement rail is a strong driving force in the direction of rotation of the guide rail Wheel body.

[0020] An advantageous ratio between the drive weight and the guide weight is, for example, 1: 4. For example, with a guide weight of 500 g and a drive weight of 125 g and a corresponding length of the displacement rail as a lever, a good drive effect can be achieved. With a wheel body with a diameter of 640 mm to max. 690 mm can have a rotation frequency of 23-25 rpm. Can be achieved.

A wheel body according to an emissionless drive according to the invention for driving a while can be considered as a motor for a generator for generating electricity or as an emission-free energy source for the mechanical operation of a pump for conveying a liquid.

According to the present invention, in the case of the emission-free drive, the wheel bodies without shear elements are to be in an indifferent equilibrium. Accordingly, the center of gravity and the center of rotation of the wheel body should be collapsed without scissor elements so that a rest position is possible in all rotational positions. Therefore, the wheel body is preferably constructed with guide rails and displacement rails so symmetrically that preferably eight identical circular cutouts are formed and two circle sections diagonally opposing each other in the wheel body form an operating unit. The wheel body is advantageously designed in such a way that, during a 360 ° rotation, at least six of the eight circular cutouts form an oblique plane on the guide rails in each position which is gradually possible.

According to the invention, a method is provided for providing an emission-free drive with a wheel body, in which a wheel body with guide rails and displacement rails is initially provided in a state of an indifferent equilibrium. Subsequently, by integrating the guide weights into the guide rails of the wheel body, the status of the indifferent equilibrium is transformed into a state of stable equilibrium. By inserting the guide weights into the oblique planes mentioned above, they roll off at the planes and the wheel body receives a deeper center of gravity so that it is in a stable equilibrium. This means that the center of gravity of the wheel body is below its center of rotation.

Further, by installing the shearing elements with the drive weights into the wheel body, the status of stable equilibrium is transformed into a driving state. In the method, it is thus provided that, after installation of the drive weights on the displacement rails of the wheel body, the state of the stable equilibrium of the wheel body is transferred by lever force into a state of unstable equilibrium.

[0024] Advantageous embodiments of the invention are described below with reference to the drawings, which serve merely for the purpose of explanation and are not to be construed as limiting. DESCRIPTION OF THE PREFERRED EMBODIMENTS Characteristics of the invention which will become apparent from the drawings are to be considered individually and in any combination as belonging to the disclosure of the invention. In the drawings:

1 shows a schematic representation of a first variant of a wheel body with an emission-free drive according to the invention, FIG.

FIG. 2 is a schematic representation of the mode of operation of the drive in the wheel body, in particular its shearing elements according to FIG. 1,

FIG. 3a shows a schematic representation of a first variant of a scissor element in a wheel body according to the invention,

FIG. 3b is a schematic representation of a second variant of a scissor element in a wheel body according to the invention, and FIG

FIG. 4 shows a schematic representation of a second variant of a wheel body with an emission-free drive according to the invention.

1 shows a first variant of a wheel body in an emission-free drive according to the invention. The wheel body has a central hub 1 with a plurality of radially extending displacement rails 2. Guide rails 3, which are arranged around the hub 1, are arranged between two displacement rails 2, respectively.

The guide rails 3 are straight and extend tangentially to the center Z of the hub 1 and at the same radial distance from the center Z. The displacement rails 2 are arranged at the same angular distance of 45 ° around the center Z. The guide rails 3 thus form a point-symmetric octagon around the center Z. The hub 1 can be coupled in a conventional manner to a shaft (not shown) in order to drive the latter.

Furthermore, the wheel body has a plurality of scissors elements 4 with scissor elements 4a, 4b, 4c and 4d which can be moved in a shear-like manner.

Each of the scissor elements 4 has a guide weight 5 at a first end which is displaceably mounted in a guide rail 3. At a second end, the shearing elements 4 have a drive weight 6. The first end is radially closer to the center Z than the second end. The guide weight 5 is arranged at a first end of the shearing member 4a. The first end of the shearing member 4a can be moved along the guide rail 3 with the guide weight 5. The shearing member 4b is fixed at its first end relative to the guide rail 3, preferably at one end of the guide rail 3. At the second ends of the shearing members 4a and 4b, respectively, the further shearing members 4c and 4d are movably mounted. Scissor movement of the scissor members 4a and 4b thus triggers a scissor movement of the scissor members 4c and 4d.

[0028] The wheel body shown in FIG. 1 is designed for a clockwise rotation. Thus, the shearing elements 4 and with them the guide weights 5 and the drive weights 6 on the right side of FIG. 1 undergo a downward movement and on the left side of FIG. 1 an upward movement as indicated by the arrows AB and AUF. At the upper and lower apexes S, the upward movement transitions into a downward movement and vice versa. As soon as a scissor element 4 passes from one movement into the other, its guide weight 5 is displaced along the associated guide rail 3 and its drive weight 6 is displaced in the radial direction, as is explained in more detail in FIG.

In FIG. 2, a shearing element 4 is shown during the transition from an upward movement UP to a downward movement AB shortly after the upper peak S has been exceeded. A further scissor element 4 'is shown in the transition from a downward movement AB to an upward movement AUF shortly after the lower vertex S' has been exceeded.

In the case of both scissor elements 4 and 4 ', the rotary movement of the wheel body during transition between the upward and downward movement causes the guide rails 3 to change their inclination direction; So that the guide weights 5 and 5 'are displaced along their guide rails 3 by means of a gravitational force from a first position P1 with a first energy level into a second position P2 with a second energy level. The second level of energy is always lower than the first level of energy. With the guide weights 5 and 5 ', the first end of the shearing members 4a is moved relative to the first end of the shearing members 4b, whereby shearing movement of the shearing members takes place and the drive weights 6 and 6' are displaced. The drive weights 6 and 6 '

In the case of an upward side ON the rotary movement, the drive weight 6 'is displaced in a radially inward position iP due to the second position P2 of the guide weight 5' On the other hand, in a downward side AB of the rotary movement, the driving weight 6 is in a radially outward position aP because of the second position P2 of the guide weight 5. It should be noted that the guide weights 5 and 5 'have substantially the same distance to the center Z both in an upwards and downwards movement and only move tangentially over the length of the guide rails 3 relative to the center Z. The radial distance between the drive weight 6 and the center Z is thus on the down side greater than the radial distance between the drive weight 6 'and the center Z on the up side.

In FIG. 2, the upper scissor element 4 and the lower scissor element 4 'are each shown in three different positions in order to illustrate the movements of the guide weights 5 and 5' as well as of the drive weights 6 and 6 '.

The upper scissor element 4 has just exceeded the upper apex point S, and the guide weight 5 moves along the guide rail 3 from the position P1 in the direction of rotation of the wheel body to the position P2; In which the shearing element 4 abuts the first end of the fixed shearing member 4b. At the same time, the drive weight 6 moves from the inner position iP into the outer position aP due to the scissor movement of the scissor members 4a, 4b, 4c and 4d. In the fully extended position aP of the drive weight 6, this can rest on the surface of the displacement rail 2 and is supported by the displacement rail 2 during the downward movement.

The lower scissor element 4 'has exceeded the lower apex point' and the guide weight 5 'comes from the position P1 counter to the direction of rotation of the wheel body to the position P2; In which the shearing element 4 'is fixed to an end stop of the guide rail 3, Is formed by the displacement rail 2. At the same time, the drive weight 6 'moves from the outer position aP into the inner position iP due to the scissor movement of the scissor members 4a, 4b, 4c and 4d. The drive weight 6 'remains with the scissor element 4' in this retracted position until both together reach and exceed the upper apex point S and the guide weight is again displaced from the position P1 to the position P2 as described above.

The guide weights 5 and 5 'and the drive weights 6 and 6' are coordinated such that the falling movement of the guide weight from the position P1 to the position P2 can exert sufficient force on the scissor members; To actuate the scissors elements 4 and 4 ', thereby lifting the drive weights 6 and 6' from the outer position aP into the inner position iP. During the rotation of the wheel body, the guide weight 5 and 5 'and the drive weight 6 and 6' are consequently displaced relative to the center Z of the hub 1 and are also balanced so that a continuous flow of force is present on the wheel body and contributes to the drive.

In FIGS. 3a and 3b, two variants of a scissor element 4 for a wheel body according to the invention are shown. Both variants are based on the function of a Nuremberg scissors. The variant according to FIG. 3a has a first pair of scissor members 4a and 4b to which a second pair of scissor members 4c and 4d are connected. A first end 4a1 of the scissor member 4a carries the guide weight 5. The guide weight 5 is designed here for example in the form of a cylinder and is rotatably mounted on the scissor member 4a. In the guide rail 3, the cylindrical shape can roll off and thus facilitates the displacement of the guide weight 5. A first end 4b1 of the scissor member 4b is fastened to the wheel body relative to the guide rail 3 in a fixed manner. The scissor members 4a and 4b are movably connected to each other in a central region along their length about a pivot point 7. At a second end 4a2 of the scissor member 4a, the scissor member 4d is articulated with a first end 4d1, and at a second end 4b2 of the scissor member 4b the scissor member 4c is articulated with a first end 4c1. The shearing member 4d is made shorter than the shearing member 4c; In the variant shown approximately half as long. A second end 4d2 of the scissor member 4d is movably connected to a central portion of the scissor member 4c about a pivot point 7. As shown in FIG. The drive weight 6 is arranged at a second end 4c2 of the shearing member 4c. The drive weight 6 is formed here for example in the form of a cylinder and is rotatable relative to the shearing member 4c. An axis of the cylindrical shape is supported in an elongated hole 8 so that the drive weight 6 can be displaced within the elongated hole 8 along the length of the shearing member 4c. The guide weight 5 and the drive weight 6 can also have a guide device which engages on the guide rail 3 and the displacement rail 2 so that the guide weights 5 are guided along the guide rails 3 during the displacement.

In an example of a shearing element 4 according to the variant of FIG. 3a, the shearing member 4a between the bearing point for the guiding weight 5 and the shearing member 4b between the articulated fixing at its first ends and the articulation at its second end can be, for example, a length of 180 mm. The shear point is provided for example 105 mm from the bearing point or the fixing. A shearing member 4c adjoining the shearing member 4b can have, for example, a length of 150 mm between the joint and the bearing of the drive weight 6, the integrated elongated hole 8 can, for example, be 30 mm long. The length of the shearing member 4d between the hinge with the shearing member 4a and the pivot point 7 on the shearing member 4c can be, for example, 75 mm. In a fully extended state, the drive weight 6 can thus be removed approximately 300 mm from the guide weight 5. The diameter of a wheel body with these specifications is approximately 600 mm.

The variant of the scissor element 4 according to FIG. 3b essentially corresponds to the construction of the variant from FIG. 3a, but is expanded by a further pair of scissor elements 4e and 4f; Which is arranged between the pair of scissor members 4a and 4b and the pair of scissor members 4c and 4d. A first end 4e1 of the scissor member 4e is movably attached to the second end 4a2 of the scissor member 4a and a second end 4e2 is movably attached to the first end 4c1 of the scissor member 4c. Similarly, a first end 4f1 of the scissor member 4f is movably attached to the second end 4b2 of the scissor member 4b, and a second end 4f2 is movably attached to the first end 4d1 of the scissor member 4d. The shearing members 4e and 4f are connected centrally in a pivot point 7. By means of the three pairs of shearing members, the drive weight 6 can thus be further removed from the guide weight 5 when the shearing element 4 is in the fully extended state. The central scissor members 4e and 4f may, for example, have the same length as the scissor members 4a, 4b or 4c. The shearing member 4 c can, however, also be designed to be longer or shorter than the other shearing members, with the exception of the shearing member 4 d.

[0039] FIG. 4 shows a second variant of a wheel body according to the invention. A section of the down side is shown. In this variant, the displacement rail 2 extends essentially radially in an inner region 13 between the hub 1 and the guide rail 3. From the guide rail 3, the displacement rail 2 is angled in an outer region 14 in the direction of rotation of the wheel body. On the downside, the displacement rail 2 in this variant is less steep for the displacement of the drive weights 6, so that the displacement into the outer position aP is facilitated. The angle between the radially extending inner region 13 and the angled outer region

Claims

Range 14 is preferably between 110 ° and 150 °. In the case of a wheel body with eight displacement rails 2, which are evenly distributed around the hub 1, the angle is preferably 95 °. The mode of operation of the second variant in FIG. 4 also corresponds to the mode of operation of the first variant, as described and described above. Reference 1 1 hub 2 displacement rail 3 guide rail 4, 4 'shearing element 4 shearing member 4 shearing member 4 shearing member 4 shearing member 4 shearing member 4 shearing member 5,5 guiding weight 6 6 driving weight swinging point 8 oblong hole 13 inner region 14 outer region Z hub, Center S, S '

The invention relates to a drive system for a wheel drive system, comprising: a central at least approximately horizontal hub having a plurality of at least partially radially extending displacement rails, and two intermediate displacement rails, Guide rails (3) arranged around the hub (1); Characterized in that it comprises a plurality of scissors elements with scissor-type scissor-type scissors elements (4a, 4b, 4c, 4d), a scissor element (4) having a guide weight (5) slidably mounted in a guide rail (3) at a first end (4a1) is; And at a second end (4c2) a drive weight (6) which is movable radially to the hub (1) by a shearing movement of the scissor members (4a, 4b, 4c, 4d); Wherein the guide weight (5) along the guide rail (3) is moved by a gravitational force from a first position (P1) with a first energy level into a second position (P2) with a second energy level which is lower than the first energy level during a rotational movement of the wheel body Is slidable along the guide rail (3), whereby shearing movement of the scissor members (4a, 4b, 4c, 4d) takes place; (6) in the second position (P2) of the guide weight (5) in a radially inward position (iP) and on a downward side (AB) of the rotary movement, the drive weight (6) Is present in a radially outward position (aP) in the second position (P2) of the guide weight (5)
2. An emission-free drive according to claim 1, characterized in that the shearing element (4) has at least two scissor members (4a, 4b) which are rotatably connected to one another; Wherein the one shearing member is fixed at its first end relative to the guide rail, and the other shearing member at its first end carries the guide weight and is movable relative to the guide rail is.
3. An emission-free drive according to claim 1, characterized in that a further scissor member (4c, 4d) is respectively mounted movably at the second end (4a2, 4b2) of the scissor members (4a, 4b); Wherein the further scissor members (4c, 4d) are connected to each other in a shear-like manner.
4. The emission-free drive according to claim 1, wherein the drive weight (6) is arranged at the second end (4a2, 4c2) of the scissor members (4a, 4b) and the further scissor members (4c, 4d).
5. Emission-free drive according to claim 1, characterized in that the guide weight (5) is cylindrical and is mounted in a rolling manner in the guide rail (3).
6. The emission-free drive according to claim 1, wherein the displacement rail extends as far as the radially outward position of the drive weight, and / or - when the drive weight (6) is extended, (6) and / or - provides support for the drive weight (6) in the external position (aP) of the drive weight (6).
7. The emission-free drive according to claim 1, characterized in that the displacement rail (2) is angled so that it extends at least approximately radially between the hub (1) and the guide rail (3) and, starting from the guide rail (3), in the direction of rotation of the guide rail (3) Wheel body is angled.
8. An emission-free drive according to claim 1, characterized in that the drive weight (6) is of cylindrical design and is provided rolling on the displacement rail (2).
9. An emission-free drive according to claim 1, wherein the guide weight (5) and / or the drive weight (6) are mounted in a floating / flying manner.
10. The emission-free drive according to claim 1, wherein the guide rails form a point-symmetric polygon, preferably an octagon, around the hub; Which has equiangular segments between the displacement rails (2).
11. Emission-free drive according to claim 1, characterized in that the guide rails (3) are arranged at the same radial distance from the hub (1).
12. An emission-free drive according to claim 1, characterized in that the drive weight (6) is lighter than the guide weight (5); Preferably a ratio of 1: 4 ascending between the drive weight (6) and the guide weight (5) is provided.
13. Emission-free drive according to one of the preceding claims, characterized in that the wheel body is in an indifferent equilibrium without scissor elements.
14. The method for providing an emission-free drive as claimed in claim 1, wherein a wheel body with guide rails and displacement rails is provided in a state of an indifferent equilibrium, wherein the guide weights are inserted into the guide body (3) of the wheel body, the status of the indifferent equilibrium is transformed into a state of stable equilibrium and - by incorporating the drive weights (6) with the scissor elements (4) into the wheel body, the state of the stable equilibrium is transformed into a driving state.
15. The method for providing an emission-free drive according to claim 14, characterized in that after the drive weights (6) are installed on the displacement rails (2) of the wheel body, the stable balance of the wheel body changes into a state of unstable equilibrium.