Method of generating Coriolis's levitation forces and a gyroscopic system ("Gyro-turbine")

BACKGROUND OF THE INVENTION 1. Field of the invention

The present invention relates to the science which studies rotating physical objects. More specifically, it concerns gyroscopic systems, including especially synchronized rotating masses, which can be used for generating plurality of Coriolis's levitation forces, having unidirectional and continuous propertys. The offered method allows to create a prime mover which is able to transfer transport means or spacecraft above planets and in observed universe without using a jet thrust of rockets or propellers.

2. Discussion of the prior art.

Coriolis's name began to appear in the literature at the end of the nineteenth century. In physical geography Coriolis's name is connected to the known Baer-Babinet law. Karl Ernst von Baer (1792-1876) was the first to publish his observation on an asymmetry of the river erosion in Russia in 1854 as a consequence of the river flow from the North onto the South simultaneously with Earth rotation around its axis. Jacques

Babinet (1794-1872) was the first to formulate (1859) correctly the regularity of the river erosion that was based on mathematical calculations and Coriolis's theory.

The term "Coriolis's force" was not used until the beginning of the twentieth century. Today, the name of Coriolis has become mainly associated with meteorology.

Laws of the air circulation and the relation between the pressure and the air streams distribution were discovered thanks to knowledge which Gaspard Gustave Coriolis (1792- 1843) had presented to us.

Coriolis's effect is an apparent deflection of a moving solid in rotating (spinning) condition. The motion of rotated solid is considered as precession. In physics, there are two types of precession, namely torque-free precession and torque-inducing precession and the latter one is an important property which could be useful for utilizing in practical purposes, for example, such as a forced precession.

Torque-inducing precession is the phenomenon when the axis of spinning solid (e.g. rotating planet) wobbles when gravitation is applied to it. The phenomenon is commonly seen in a spinning toy top, but all rotating objects can undergo precession.

The second important property of rotating solid is nutation, i.e. a slight mainly irregular "nodding" in the axis of rotation of a largely symmetric object, such as the above mentioned spinning toy top or a planet rotating around its axis.

The observation of the Coriolis's effect can be carried out in such a way: the spinning ball moves over a rotated platform, such as a roundabout from its outside to the center of the rotated platform (http://en.wikipedia.org/wiki/coriolis_force). The anomalous deflection of such a ball during the observation of the Coriolis's effect occurs because of an inertial force which has been referred to Coriolis's forces

The Coriolis's force is known to depend on four things: the angular frequency ω of rotation of an object, the mass of the object (m), the precession velocity of the object (V) and the precession angle (φ) by which the object is moving with respect to the rotation. An expression usually used for the Coriolis's force is:

F _k =2mω V SIN (φ). (1)

The forced precession is an especial motion of rotated object with respect to the second axis (precession axis) caused by an external nongravitational force. In other words, such a precession refers to forced change of the axis orientation of rotating object.

The Coriolis's force can perform real work, though some scientists consider it as a fictitious force which is not able to work. The useful work of the Coriolis's force takes place in a grinding mill (FIG.l), where a heavy grinding cylinder 1 is established on a portable shaft 2 with the possibility to rotate while running over a mill plate 3. The cylinder 1 rotates around the first portable axis X (4) in the direction of an arrow A. The portable shaft 2 is connected to a vertical shaft 5 with the possibility of deflecting in the vertical direction with respect to a pivot axis 6. The vertical shaft 5 is rotated by an engine 7 around the third vertical axis Z which is labeled in FIG.l as a position 8. Three axises X, Y, Z create in FIG.l an orthogonal system. (B.A.IIaBJioB 'THpocκoπEraecκHH 3φφeκτ." JIeHHHrpa,zi;. ,,Cyflocτpoemie" 1967r., pp. 251,252).

If the vertical shaft 5 is rotated by the engine 7 in FIG.l, for example, clockwise with angular velocity ω around the third axis Z (8), the grinding cylinder 1 is rolling on the mill plate 3 with angular frequency ω > ω .

The motion (caused by a force produced by the engine 7) of grinding cylinder 1 around the axis 8 simultaneously with rotation of grinding cylinder 1 around the axis 4 is the above mentioned forced precession. During such a complex motion of grinding cylinder 1 a force F _k is appearing which is directed vertically downwards along the axis

5 Z (8).

This force F _k is the above mentioned Coriolis's force. The mass of grinding cylinder 1, being acted upon by this inertial force F _fo presses the grinding cylinder 1 to the mill plate 3 in such a way destroys the structure of the material distributed over the plate 3.

10 The angle 9 between the velocity vector V and rotational vector ω in FIG.l is the above mentioned precession angle φ.

The direction of the Coriolis's force F _k can be determined by the known Zhukovsky's rule (H.E.3KyκoBCKHH "KHHeMaTmca. Cτaτiiκa. /JimaMHKa TOHKH" MocKBa, O6OPOHγH3, 1939r. - ρρ.67,68).

^ For determining the direction of the Coriolis's force F _k according to the above mentioned Zhukovsky's rule it is necessary to turn conditionally on 90° the velocity vector V of the said grinding cylinder 1 in the direction A of the rotation of grinding cylinder 1. The conditionally turned vector v defines the orientation of the force F _to that is directed downwards along the vertical axis 8 in FIG.l. ^zυ Such a grinding mill can be considered as three-axis (X,Y,Z) gyroscopic apparatus where the Coriolis's force is utilized to perform real grinding work.

Coriolis's forces cause another known phenomenon, namely so-called gyroscopic couple (below mentioned as gyro-torque) utilized in a Momentum wheel which is shown in FIG. 2.

^δJ The gyro-torque M in FIG.2 is appearing in a flywheel 1 which is rotated by an engine (not shown) around the first horizontal axis 4 simultaneously with pivoting of the flywheel 1 with respect to the vertical axis 8, passing through a mass point Q of the flywheel 1. The vertical axis 8 in FIG.2 is established perpendicularly to the first axis 4.

In this case a couple M is appearing, trying to twist the rotating flywheel 1 around

™ the second horizontal axis Y (6).

The gyro-torque M is caused by action of a pair of the Coriolis's forces F _k , -F _k on the opposite parts of rotating flywheel 1 as it is shown in FIG.2. Forces F _to -F _k are

focused opposite to each other along the horizontal axis 4 and they cause the gyro-torque

M in FIG.2.

The gyro-torque phenomenon is utilized now in powerful gyroscopes (see, for example, the patent of the Russian Federation Na95120281 "Hydro-dynamical Gyroscope" dated 1997.10.27, Int.Kl. G01C19/00) and in the so-called CMG (Control

Moment Gyroscope), which are used to control orientation of spacecraft (for example, the patent of the Russian Federation N° 1839792 "The powerful Gyroscopic Device for

Orientation of Space Apparatus in Space" dated 2005.05.10, IntCl. B64G1/28,

G01C19/00). In the above mentioned patents different gyroscopic devices are described, where massive flywheels (or rotors) are established, rotating with a big angular frequency

(3000OmUi ^"1 and more).

Such a device can be considered as two-axis (X,Z) gyroscopic apparatus that can turn transport means or spacecraft to change their orientation without utilizing a jet thrust of a rocket.

The next known device is developed to avoid a gyro-torque reaction. It comprises casing with inside established motor and a gimbal with the flywheel that is coupled to a motor by a gear transmission. There are loads eccentricly established on pinions of the gear transmission. Inside the gimbal on a carrier shaft a gyro-motor is established tilted to the gimbal axle; the said carrier shaft is coupled by hinges to the gimbal and to axles of pinions (patent of the Russian Federation N°2084826 "Gyroscopic-Centrifugal

Device", dated 1997.07.20, IntCl. GOlCl 9/02, B64G1/28).

This known device generates the above mentioned gyro-torque, that allows to change the spacecraft orientation without presence of the gyro-torque reaction. But such a gyroscopic device is not able to move the spacecraft rectilinearly in the predetermined direction.

Alexander D. Kidd had utilized pulsation of angular momentum to generate gyroscopic nutation forces that can be used to move spacecraft rectilinearly without jet thrust of the rocket.

In his USA-patent Ne 5,024,112 dated June, 18, 1991 a gyroscopic apparatus (shown in FIG.3) is described, comprising a pair of spinning disks Ia ₅ Ib disposed

opposite one another on portable shafts 2a, 2b with L-shaped arms 10a, 10b, which support rotating disks Ia, Ib in bearings. Supporting L-shaped arms 10a, 10b are disposed on the vertical shaft 5 similar to the above mentioned grinding mill in FIG.l connected at a pivot point of the second axis 6 thereof lying in a plane midway between disks Ia, Ib. A drive means (it is not shown) operates to spin disks Ia ₅ Ib around two local axises 4a, 4b in the opposite directions with angular rotation frequence ω simultaneously with rotation by engine 7 the whole assembly of disks Ia ₅ Ib and arms 10a,10b around the vertical axis 8 with precessional angular velocity ω in the same plane but perpendicularly to the pivot axis 6. Camming arrangement 11 works in conjugation with the rotation by the engine 7 around the second axis 8 periodically forces the spinning disks la,lb to deflect together with arms 10a,10b about the pivot axis 6 to thereby generate a pulsative thrust force along the second axis 8.

Arms 10a, 10b are oscillated by the camming arrangement 11 in a working condition of the gyroscopic apparatus; the mass point c (12) of the disk Ib is performing a motion along a trajectory 13 which is disposed on the sphere 14, having a radius r designated in FIG.3 as 15. The angle between the said vertical axis 8 and the said local axis 4a (4b) is changing during the forced precession. The specified radius r is equal to the distance from the mass point 12 (c) up to the intersection point Q of axises 8 and 6. The axis 4b (also as the axis 4a) together with the mass point c (12) are moving up along the three-dimensional undulating surface 16 (radially hatched in FIG.3); the spinning disk Ia (Ib) is deviating periodically from its top position Ia to the bottom position Ic (Id) that is shown in FIG.3 in dotted lines.

The motion of axises 4a, 4b of both disks Ia, Ib along the trajectory 13 can be considered as an artificial created nutation. The nutation trajectory 13 of the mass point c (12) is disposed on the sphere 14 between circles 17 and 18 which allow to determine the amplitude A, that is the first parameter of the nutation. The amplitude A of the artificial nutation depends on the camming arrangement 11 which deflects arms 10a, 10b about the pivot axis 6 by motion links 19. The second parameter of the trajectory 13 is nutation frequency ε that determines quantity n of swinges between circles 17, 18 during one completed turn of the vertical

W shaft 5 around the precession axis 8. For example, in FIG.3 eight swinges are shown and therefore n=ε/ω that is equal to eight.

The disks motion along the trajectory 13 produces a gyroscopic couple T _g to be applied to disks Ia ₅ Ib along the axis 8 by virtue of the relationship between torque and change in angular momentum L of rotating disk Ia (Ib), as stipulated in equation below:

T _g = dL/dt.

The direction of the gyroscopic couple T _g ^c (T _g ^d ) in the bottom position Ic (Id) of rotating disk is not equal to the direction of the gyroscopic couple T _g ^a (T _g ^b ) in the top position of rotating disks Ia, Ib. Therefore, the gyroscopic thrust force, directed upwards and produced by the motion of rotating disk Ia (Ib) along the piece DE of the trajectory 13 is bigger than the gyroscopic thrust force produced by the motion of rotating disk Ia (Ib) along the piece EF of the same trajectory 13.

As a result, the known gyroscopic apparatus in FIG.3 is able to generate a pulsative levitation force with frequency ε = nω.

Disadvantages of the known method as well as the above mentioned gyroscopic apparatus are followings:

(i) the high level vibration in the vertical direction (along the axis 8);

(ii) impossibility to utilize in practice more than two rotating masses (Ia, Ib) to increase the thrust power.

In other words, there are all preconditions now to compensate the gyro-torque and generate plurality of Coriolis's unidirectional forces in a gyroscopic system that can perform real work to move transport means in the predetermined direction without vibrations with huge levitation power. Therefore, the first aspect of the offered invention is the method of generating plurality Coriolis's forces for continuous movement of an apparatus in water, in air (in Space) without thrust vibrations.

The second aspect of the offered invention is the development of the gyroscopic system that is able to transform torque, produced by a machine (for example, by an electric motor), into continuous, uniform (not pulsative) Coriolis's levitation forces with high efficiency.

I offer to refer to such a gyroscopic system as a "Gyro-turbine".

GENERAL DESCRIPTION OF THE INVENTION

With the purpose of generating Coriolis's forces a method, including a rotation around a local axis of at least one object, producing a rotational frequency vector ^~ αξ simultaneously with forced precession of the said object, having a mass M, around a precession axis with precessional velocity V which according to my proposal comprises: a) the step of moving a mass point of the said object during the said forced precession along a primary flat trajectory; b) the step of supporting a constant angle ψ between the said local axis and the said precession axis; c) the step of providing an integer ratio i = ωA/V = ω/ωi of synchronization during the said forced precession between the said angular frequency ω and the said precessional velocity V; where: A ₄ - is a distance from the said mass point of the said object up to the said precession axis; ωj = V/Aj - is an instant angular velocity of the said forced precession of the said object, producing a precessional vector ω; d) the step of coordinating dimensions of the said object depending on the said distance A ₁ from the said precession axis up to the said mass point of the said object.

Preferably, the offered method consists in utilizing the said object, providing a size ratio L>D; where L - is a length of the said object along the said local axis; D - a maximal outer diameter of the said object; in coordinating the value of respective mass part mi of the said object depending on the distance A ₁ from the said precession axis up to the said mass part of the said object according to a mass distribution law nii=f(Ai).

Preferably, the offered method consists in utilizing the said mass distribution law in a view: mi = M/A _{ ; where M - is the said mass of the said object. Preferably, the offered method consists in utilizing combination of the plurality of working rings and disks as the said one object.

Preferably, the offered method consists in spinning of the said object according to a specifying rule, including the step of providing the said rotation of the said object in the direction, at which the said rotational frequency vectoflfr has to coincide with a vector Q' combined with the said local axis by a turn of the said precessional vector ω around an intersection point Q of the said local axis and the said precession axis.

Preferably, the offered method consists in utilizing an elliptic trajectory as the said primary flat trajectory; in providing balance of angular energy E _|| (ω) of the said rotation of the said object with kinetic energy E±(V) of the said precession of the said object. Preferably, the offered method consists in utilizing a circular trajectory as the said primary flat trajectory; in providing the integer ratio i = ω/ω during the said forced precession between the said angular frequency ω and angular velocity ω of the said precession; in providing balance of the said angular energy E _|| (ω) with angular energy Ej_(ω) of the said precession of the said obj ect.

Preferably, the offered method consists in coordinating a value of the said angular frequency ω with the said distance A ₁ ; in coordinating the said mass M of the said object with the said frequency ω.

Preferably, the offered method consists in utilizing the said ring with a conic inner surface as the said object, having an outer diameter Dj which is defined as d _t - is an inner average diameter of the said ring; A _{ - is the said distance from the mass point of the said ring up to the said precession axis; ω - is the said angular frequency; ω - is the said angular velocity.

An improvement of the method according to the proposal, consists in utilizing a group of an odd quantity N of working solids, not less than three; in allocating the said working solids around respective local axises; in rotating each of the said working solids around the respective said local axis according to the said specifying rule; in establishing the said local axises on equal angular distances from each other around the said precession axis; in coordinating the said integer ratio i=ω/ω with the said quantity N of the said working solids.

Preferably, the offered method consists in utilizing at least a part of a working cone as the said object; in focusing an apex of the said working cone in the direction of the said precession axis.

Preferably, the offered method consists in utilizing fluid as the said object and in transfer of the said fluid along a secondary trajectory around the said local axis.

Preferably, the offered method consists in establishing the said secondary trajectory in a plane, which is inclined with respect to a vector V of the said velocity V of the said forced precession at an angle that is not equal to π/2.

Preferably, the offered method consists in transfer of the said fluid along an elliptic secondary trajectory around the said local axis.

Preferably, the offered method consists in utilizing mercury as the said fluid.

Preferably, the offered method consists in utilizing charged particles as the said fluid and in transfer the said charged particles along an elliptic secondary trajectory around the said local axis. Another improvement of the method according to the proposal, consists in utilizing an even number 2N of the said objects not less than four; in allocating the said objects around respective separate local axises; in rotating each of the said objects around the respective said separate local axis according to the said specifying rule; in distributing the said objects at least onto two groups, containing N number of the said objects; in moving the first said group of the said objects around the said precession axis clockwise; in moving the second said group of the said objects around the said precession axis counterclockwise; in establishing the said local axises on equal angular distances from each other around the said precession axis; in coordinating the said integer ratio i=ω/ω with the said quantity N of the said objects in the respective said group in such a way, that the said quantity N is equal to the said integer ratio i.

Preferably, the offered method consists in providing the said forced precession in a rarefied gaseous enviroment.

Preferably, the offered method consists in providing the said angle ψ between the said local axis and the said precession axis from a range 90°< ψ < 180°. A gyroscopic system (gyro-turbine) for generating Coriols's forces including a transport platform, an engine established on the said transport platform, at least one working solid rotated around a local axis with angular frequency ω by a drive means

simultaneously with forced precession around a precession axis with angular velocity ω according to my proposal comprises a precession unit for supporting and moving the said working solid around the said precession axis along a circular primary trajectory; a synchronizing unit for coordinating the said angular frequency α> with the said angular velocity ω to provide balance of rotational angular energy E _|| (ω) of the said working solid with precessional angular energy E_L(ω) of the said working solid.

Preferably, the said synchronizing unit comprises the first tachometer to measure the said angular velocity ω; the second tachometer to measure the said angular frequency ω; a controller unit to regulate rotation frequency of the said drive means.

Preferably, the said synchronizing unit provides an integer ratio i=ω/ω, during the rotation of the said working solid around the said local axis in the direction, at which the said rotational vector ed coincides with a vector ω' combined with the said local axis by a turn of the said precessional vector ω around an intersection point Q of the said local axis and the said precession axis.

Preferably, the said working solid is a combination of rings established on a common portable shaft; each said ring has an outer diameter D defined as D=V2A ² /i ² -d ² , where d is an internal diameter of the said ring; A is the distance from a mass point of the said ring up to the said precession axis; i - is the said integer ratio. Preferably, the said working solid is a part of a cone, having an apex, focused in the direction of the said precession axis; the said cone having a base with a diameter D defined as D=kU/i; where U - is the distance from the said base up to the said precession axis; i - is the said integer ratio; k>2 is a dimensionless factor.

Preferably, the said precession unit is a supporting rigid star-shaped structure, having vertexes, carrying an odd number of the said working solids, being not less than three; working solids having possibility to rotate around the respective said local axises on vertexes of the said star-shaped structure, connecting to an output shaft, having the possibility to rotate around the said precession axis by the said engine.

Preferably, the said synchronizing unit provides an integer ratio i=ω/ω=N of synchronization; where N is equal to the quantity of the said working solids.

Preferably, the said local axises are disposed on equal angular distances from each other around the said precession axis.

Preferably, the said working solid is rotated around the said local axis by a separate motor.

Preferably, the said local axis is disposed with respect to the said precession axis at an angle ψ, which is chosen from a range 90° <ψ <180°. Preferably, the said precession unit is established in a rarefied gaseous environment.

Another embodiment of the gyro-turbine including a casing, working solids, rotating around respective separate local axises with angular frequency ω by a drive means simultaneously with forced precession around a precession axis with an angular velocity ω according to my proposal comprises a precession unit for supporting and moving the said working solids along a flat primary trajectory; a coordinating unit, providing an integer transmitting ratio i for balance of rotational angular energy E _|| (ω) with precessional angular energy E_ _L (ω) of the said working solids; a sealant means for providing a rarefied gaseous enviroment inside the said casing during the said forced precession of the said working solids.

Preferably, the said coordinating unit is a mechanical transmission, providing a kinematical connection of the said working solids directly to the said casing. Preferably, the said coordinating unit is a helical gear transmission.

Preferably, the said coordinating unit is a friction transmission. Preferably, the said precession unit includes displacement means, providing a shift of the said working solid along the said local axis to change a radius of the said primary trajectory for regulating balance of rotational angular energy E _|| (ω) with precessional angular energy Ej_(ω).

Preferably, the said working solid is a part of a working cone, having an apex, focusing in the direction of the said precession axis; the said working cone having a base diameter D defined as D=kU/i, where U - is the distance from the said base up to the said precession axis; i - is the said transmitting ratio; 2 < k < 5 is a dimensionless factor. Preferably, the said working cone is rotated around the said local axis by a separate electric motor.

Preferably, the said precession unit, including at least three rotated said working cones, comprises at least two flat rigid disks for supporting the said working cones; supporting means for orientation of the said working cones between the said disks along the respective said separate local axises, the said flat rigid disks are established in the said casing with the rotation possibility around the said precession axis to provide the said precession of the said working cones around the said precession axis.

Preferably, the said precession unit, including an even number of the rotated said working cones, comprises at least two carrier means, established with the rotation possibility around the said precession axis; an even number of primary and secondary portable shafts, not less than four, supporting the said working cones, which are quantitatively equal to the quantity of the said portable shafts; each of the said working cones is established in bearings at an outer end of the respective said portable shaft, allocated coaxially with respect to the said local axis; all primary said portable shafts are fixed in the first said carrier means with the movement possibility around the said precession axis by the first said carrier means; all secondary said portable shafts are fixed in the second said carrier means with the movement possibility around the said precession axis by the second said carrier means; said carrier means are established in the said casing with the rotation possibility around the said precession axis in the opposite directions.

Preferably, the said local axises are disposed on equal angular distances from each other around the said precession axis.

Preferably, the said portable shafts are disposed with respect to the said precession axis at an angle ψ, which is chosen from a range 90° < ψ < 180°.

Preferably, the said mechanical transmission is established in the most outer part of the said working cone.

BRIEF DESCRIPTION OF THE DRAWINGS FIG.l is a perspective view illustrating the known grinding mill.

FIG.2 is a perspective view illustrating the known Momentum wheel. FIG.3 is a perspective view illustrating the known gyroscopic apparatus.

FIG.4 is a diagram illustrating the principle of generating Coriolis's forces by one working object.

FIGs 5,6 are diagrams illustrating the offered form of the working solid. FIGs.7,8 are diagrams illustrating the principle of generating Coriolis's forces by plurality of working solids.

FIGs 9,10 are diagrams illustrating an example of utilizing a fluid to generate Coriolis's levitation forces.

FIG.ll is a diagram illustrating an elliptic motion trajectory of the working fluid. FIG.12 is a perspective view of a plasma sphere, generating Coriolis's forces.

FIG.13 is a perspective view illustrating the first embodiment of the offered gyroscopic system utilizing the offered method.

FIG.14 is a diagram illustrating an embodiment of the synchronizing means for coordinating angular frequency of the rotation with angular velocity of the precession. FIG.15 is a diagram illustrating the improvement of the offered method.

FIG.16 is a sectional view of the second embodiment of the offered gyroscopic system.

FIG.17 is a top view of the section along a line A-A according to FIG.16.

FIG.s 18,19 are sectional diagrams, illustrating the improvement of the offered gyroscopic system.

FIG.s 20,21 are sectional diagrams, illustrating the offered gyro-turbine.

DESCRIPTION OF THE PREFERRED EMBODIMENT

The offered method is based on the principle of generating plurality Corioli's forces as it is shown in FIGs. 4,5 and 7.

There is working object 20, having a mass M in FIG.4, performing rotation 21 in a direction 22 with angular frequency ω around an axis 23 simultaneously with precession 24 caused by a precessional force F _p . The axis 23 will be further referred to as a local axis. The working object 20, having an outer diameter 25 quantified by a value D, is performing the precession around a vertical axis 26 (Z) with respective precessional velocity Vi 27 along a primary flat trajectory 28 disposed in a geometrical plane 29. The vertical axis 26 will be further referred to as a precession axis. The said local axis 23 is

tilted with respect to the precession axis 26 at an angle 30 - ψ that is constant during the said forced precession. The working object 20 is moving with respect to the precession axis 26 on an average distance 31 in gaseous environment labeled as 32 in FIG.4.

According to the offered method the value of the said angular frequency ω is coordinated with the said precessional velocity Vi in such a way that an integer ratio i=ωAi/Vi is observed; where A ₁ - is the said distance 31 from the mass point 33 of working object 20 up to the precession axis 26. The said mass M of the said working object 20 is chosen depending on the said distance 31 (Aj) from the precession axis 26 up to the mass point 33 of the said working object 20. Such a coordination is the first characteristic feature of the offered invention which will be explained below (page 17).

The precession trajectory 24 in FIG.4 can be a part of an ellipse 28 that is disposed completely in the plane 29. The ellipse 28 forms the said primary closed trajectory of the forced precession 24. According to the offered invention the working object 20 can be considered as consisting of the plurality of rotated working solids 34 which are separate parts of the said working object 20 (for example, there are eight parts 34 _{ of working object 20 in FIG.4 and therefore i = 1,...,8). The mass of the each part 34 is quantified by a value nii.

The outer diameter D (25) of working object 20 in FIG.4 is less than its length 35 along the said local axis 23, namely D<L; where L - is the said length 35. Such a size ratio L>D is the second characteristic feature of the offered invention.

At such a complex motion of the each part 34j of working object 20 a Coriolis's force Fa is appearing, which is directed upwards according to Zhukovsky's rule along the precession axis 26 (perpendicularly to the vector v 27 of the precessional velocity V ₁ and of the angular frequency vector eT 36).

The numeric value of the force F _ω can be calculated according to (1) as

F _ki =2m _i ωV _i SIN (90°), because the angle φ between equal to 90° in FIG.4.

According to the offered method each part 34i...34j...34 ₈ of the said working object 20 generates an identical value F _ω of Coriolis's force, namely (4)

Providing such an equality (4) is possibly by coordinating the above mentioned mass Hi; of the respective part 34 _t of the said working object 20 depending on the distance Aj (31) according to a mass distribution law for example, by decreasing the mass mi of the each part 34j of working object 20 with increasing in its distance Aj from the precession axis 26, namely where M - is the above mentioned total mass of working object 20.

Distributing of the said working object 20 along the local axis 23 according to a law nij=f(Ai) is the third characteristic feature of the offered invention. The ratio between Vi and Ai defines an instant angular velocity ω of the forced precession around the axis 26. If to take into account that we can receive: SIN(90°)=Mωω SIN (90°) = const at fixed values M, ω and ω.

Hence, it is enough to utilize only one unique working object 20 to generate a plurality of identical forces F _ω ; i=l,8, acting upon the said total mass M of the working object 20 along the vertical axis 26. These forces F _ω can be utilized to move the said working object 20 along the axis 26 in the vertical direction. The plurality of identical forces F _ω ; i=l,8 provides motion of working object 20 plane-parallel in the vertical direction (along the axis 26) because they work uniformly along the local axis 23. In such a case the above mentioned expression "the opposite established mass" which is claimed in USA-patent Ns5 024 112, loses its sense because the said working object 20 has no working mass placed opposite.

Therefore the rotation 21 in the direction 22 of working object 20 is coordinated with the direction 34 of the forced precession 24 according to a specifying rule offered by me.

The offered specifying rule orders to tilt conditionally the vector 37 (ω) of the above mentioned angular velocity ω of the forced precession (that is directed vertically upwards in FIG.4 around the point 38 of the intersection of axises 23 and 26 to combine with the local axis 23 along a trajectory 39 and the direction 40 of the rotational vector ω 36 has to coincide with the direction 41 of the tilted vector ω' (the intermediate position of the vector ω' is shown in FIG.4 as a dotted arrow).

The offered specifying rule provides appearing of Coriolis's levitation forces directed upwards.

The said working object 20 in FIG.4 can be a combination of the plurality of working solids as it is shown in FIG.5. For example, there are two disks 42a, 42b and six rings 43 which are established parallelly on a common portable shaft 44 along the said local axis 23 in FIG.5.

Such a combination of working solids 42, 43 established parallelly on a common portable shaft 44 is the next characteristic feature of the offered invention.

Lateral working solids 42a and 42b in FIG.5 are manufactured in form of a disk connected to the common portable shaft 44. The lateral disk 42b, as it shown in FIG.6, is constructed so that the most of its mass is concentrated on the rim 45 of the disk 42b. This concentration is assisted by providing holes 46 in the disk 42b between the portable shaft 44 and the rim 45. This gives the disk 42b a larger component of angular moment of inertia for a given rotation frequency ω. Inner solids 43χ...43i...43 ₆ are manufactured in form of a ring coaxially disposed with respect to the local axis 23.

The rim 45 of the inner ring 43i (i= 1...6) in FIG.5 is allocated with respect to the conic surface 47 in such a way, that the angular moment of inertia of the rim 45 above the surface 47 is equal to the angular moment of inertia of the rim 45 below the surface 47. Inner rings 43i (i= 1...6) can be connected each to other and to lateral disks 42a and 42b by plurality of pins 48. The inclination angle α of the conic surface 47 is defined by above mentioned synchronizing ratio i=ω/ω.

As it is clearly visible in FIG.4 Coriolis's forces F^ ; i=l,8 are a consequence of the above mentioned precessional force F _p because the latter one is a cause for the forced movement of working object 20 with the precessional velocity Vi.

I have investigated transforming efficiency of the precessional force F _p into the Coriolis's force F _ω .

My investigation has discovered following facts.

The part 34 of the said working object 20 in FIG.4 (as well as working solids 42,43 in FIG.5), having a fixed mass mi and rotating around the local axis 23, is quantified by rotational angular energy E^ that is expressed as the product of the angular moment of inertia I _iif of the part 34 (42) and its angular rotational frequency ω

The angular moment of inertia I^ for the part 34 in a form of a disk 42 or a ring 43 in FIG.5 can be found as the product of three components: which refers to the fact that rotating part 34 (42,43 in FIG.5 ) maintains its state of uniform rotational motion around the local axis 23; K ₁ = 0.5 - is a factor reflecting a ring-shaping configuration of the part 34i (or the ring 43 in FIG.4).

On the other hand, the same part 34 (42) with the fixed mass Di ₁ , moving with respect to the precession axis 26 is quantified also by linear (kinetic) energy Eu. of the forced precession that is expressed as the product of the mass nij of the part 34 (42) and its precessional velocity Vj

I have discovered that the above mentioned rotational angular energy of the part 34 (42) has to be coordinated with kinetic energy the forced precession in such a way that an equality E _J U = Eu is observed for achieving a maximal transfer efficiency from the above mentioned precessional force F _p up to the Coriolis's levitation force Fy.

If to take into account that VJA ₄ =Q ; I have received 0.Sm ₁ Q ² A ₁ ² ; where

According to the equality (6) the offered method includes the step of coordinating angular frequency ω with above mentioned precessional velocity V ₁ of the said working object 20.

The equality (6) defines as well the above mentioned synchronizing ratio i = ωA/V which is provided during the said forced precession of the said working object 20 in FIG.4. Besides, according to the equality (6) the offered method includes the step of coordinating the value of the angular frequency ω with the angular velocity ω of the forced precession of the said working object 20.

According to the equality (7) the value of the Coriolis's force depends on a step of coordinating the distance A ₁ (31) with the outer diameter D=2R (25) of working object 20 that defines the respective angular rotational energy Ei _|| =0.5Kinii© ² R ² .

The equality (7) allows to define the outer diameter D (25)of working ring 43 in FIG.5 depending on its inner diameter 49 as follows: (0.5<f<0.95); A - is the said distance 31 from the said mass point 33 of the said ring 43 up to the said precession axis 26; di - inner diameter 49; ω - is the said angular frequency of rotation, ω - is the said angular velocity of precession.

The forced precession 24 in FIG.4 can be not only a part of the elliptic trajectory 28 as an exclusive motion kind of working object 20 around the precession axis 26.

The said rotated working object 20 can be moving during the precession along a circular trajectory 28c (FIG.4) or a spiral trajectory 28s around the precession axis 26. The possibility to change the circle radius A (31) of the said precession trajectory 28 is described further on an example of a gyro-turbine embodiment.

The present invention offers to provide the said synchronizing ratio i = ω/ω during the said forced precession of working object 20 around the precession axis 26 in such a way that i is an integer, chosen from a range 2<i<12; where ω - is the said angular frequency; ω - is the above mentioned angular velocity of the said forced precession.

The next characteristic feature of the offered invention is the regulated balance of rotational angular energy Ey(ro) of the said working object 20 with angular energy Ej_(ω) of the precession of the said working object 20 in such a way that an equality Ey(ω) = nEχ(ω) is observed, where n - is a dimensionless factor that is chosen from a range

0.5<n<1.5.

The gaseous environment 32 in FIG.4 creates resistance with respect to the precessional movement of the said object 20 around the precession axis 26. The gaseous environment 32 decreases the transforming efficiency of the precessional force F _p into the Coriolis's force F _ω .

Therefore, the presented here method offers to provide the said forced precession in rarefied gaseous environment or in vacuum to decrease the resistance of the enviroment 32 against the precessional motion of working object 20. If to utilize a lot of working objects 20 in FIG.4, allocated around the said precession axis 26, the total value of the plurality of Coriolis's unidirectional forces has to increase and the offered method allows simply to utilize any quantity of working solids 42, 42a, 42b, (for example, disk-shaped solids similar to the known gyroscopic

apparatus in FIG.3), as it is shown in FIG.7, which are performing the forced precession around the axis 26 along circular trajectory 28 (28b). The quantity N of working solids 42 in FIG.7 is equal to an odd number not less than three.

Working solids 42, 42a, 42b are quantified by respective masses, namely M ≠ Ma = Mb, rotating around the respective separate local axises 23, 23a, 23b. Local axises 23, 23a, 23b in FIG.7 can be disposed on different angular distances α, β and γ around the precession axis 26 that is the next characteristic feature of the offered invention. In such a case the above mentioned expression "opposite established mass" which is claimed in USA-patent N°5 024 112 also loses its sense because, for example, the said working solid 42 in FIG.7 has no working mass placed opposite along the local axis 23.

Therefore, each working solid 42 (42a, 42b) in FIG.7 is rotated around respective local axis 23 (23a, 23b) according to the above mentioned specifying rale with respective frequence ω, ω _a , G>I,; (ω ≠ ω _a = ωj,) simultaneously with precessional motion, having respective precession velocity V=ωA; Va=ωB; Vc=ωC; where A, B, C (A<B=C) - are radii 31, 31a, 31b, defining the respective distances from the common precession axis 26 up to the respective mass point 33 (33a, 33b) of working solid 42 (42a, 42b).

According to the above mentioned specifying rale it is necessary to tilt conditionally the vector ω (37) of the forced precession (that is directed vertically upwards in FIG.7) around the point 38 of the intersection of axises 23 and 26 to combine, for example, with the local axis 23b along the trajectory 39 and the direction 40 of the rotational vector oo _b 36 has to coincide with the direction 41 of the tilted vector ω' (the intermediate position of the vector ω' is shown in FIG.7 as a dotted arrow). If to apply the offered specifying rale to each working solid (42, 42a, 42b), all rotational vectors of working solids 42 will be directed outside with respect to the precession axis 26, i.e. all rotational vectors ^" of should have centrifugal directions as it is shown in FIG.7.

Each local axis 23, 23a, 23b in FIG.7 can be disposed with respect to the precession axis 26 at the constant angle ψ 30 that is chosen from a range π/2 < ψ <π. In such a case the local axis 23 is moving along a conic surface 47a (radially hatched in FIG.7) together with the mass point 33 of working solid 42. The same is true for other local axises 23a, 23b. The mass point 33 of working solid 42 is moving during the precession along the trajectory that is a part of the circle 28 allocated on the same

conic surface 47a. Simultaneously, the circle 28 is disposed in the geometrical plane 29 which is hatched in part by the plurality of parallel lines. In this geometrical plane 29 all radii 31, 31a, 31b, all angles α,β,γ, and an intersection point R are disposed. As a result, the intersection point 38 of axises 23, 23a, 23b is disposed above the point R. The complex motion of working solids 42, 42a, 42b in FIG.7 generates Coriolis's forces F _k , F^,, F _kb directed upwards according to Zhukovsky's rule along the precession axis 26. The numerical value of the force F _k can be calculated according to (1) as

F _k =MωV SIN (90°) COS(ψ)=MωωA COS(ψ); where A - is the said distance from the mass point 33, of the solid 42, up to the common precession axis 26.

The Coriolis's force F _k in FIG.7 produces a gyroscopic torque T, defined as

T= F _k *A that can be a cause for a periodical deflection of the axis 23 with respect to the axis 26 in FIG.7 during the forced precession of disk-shaped working solid 42.

To avoid such a deflection the said working solid 42a (42b), having a mass M _a (M _b ), is moving around the same precession axis 26 with the another precessional velocity V ₃ (V _b ) simultaneously with rotation around the respective local axis 23a (23b) with rotational frequency ω _a (ω _b ). Working solid 42a (42b) is moving along the circular trajectory 28a (28b).

If to apply the Zhukovsky's rule to motion conditions of the additional working solid 42a (42b) it will be possible to define the direction of an additional Coriolis's force

Fkas (F _k b) tftøt ^acts upon the mass of working solid 42a (42b).

According to the Zhukovsky's rule the velocity vector 27 V _a (V _d ) of the forced precession should be turned conditionally in the rotation direction of the vector ^~ c^ _a ((%) on 90° and such a turned vector V _a (V _b ) shows the direction of the additional Coriolis's force F _ka (F _kb ), acting upon each working solid 42a (42b).

The numerical value of the force F _ka can be calculated according to (1) as:

F _kb =M _a ω _a ωB COS(ψ).

The numerical value of the force F _kc is calculated according to (1) as:

F _kb =M _b ω _b ωC COS(ψ).

As it is clearly visible in FIG.7, three continuous forces F _k , F _ka and F _k j, are acting coordinated in one direction along the precession axis 26. These forces can move rotating solids 42, 42a, 42b with a total levitation force F _k +F _ka + F _kb .

But the plane-parallel movement of disk-shaped working solids 42, 42a, 42b along the precession axis 26 in FIG.7 would be possible if, for example, the condition

T= F _f c _a RE + F _kb RF is observed along the projective line 33-E of the axis 23 in the plane 29; where RE = B cos(π-α) - is the distance between points R and E in FIG.7; RF = C cos(π-γ) - is the distance between points R and F and therefore MωVA=M _a ω _a V _a Bcos(π-α)+M _b ω _b V _b Ccos(π-γ)=M _a ω _a V _a B(cos(π-α)+cos(π-γ)) while M _a = M _b ;C=B; ω _a =ω _b ; γ = α or, that is the same, ω/ω _a = V _a /V* (B/A) *M _a /M*2cos(β/2) (8)

Therefore, according to the equality (8) the offered method of generating

Coriolis's forces includes the step of coordinating angular rotational frequencies ω,ω _a with precessional velocities V, V _a .

The next step of the offered method according to the equality (8) consists in coordinating angular frequencies ω,ω _a with distances A, B from the above mentioned mass points 33, 33a (33b) of working solids 42, 42a (42b) up to the precession axis 26.

Another step according to the equality (8) consist in coordinating angular frequencies ω, ω _a with masses M, M _a of working solids 42, 42a(42b).

The next step of the offered method according to the equality (8) consists in coordinating angular frequencies ω, ω _a with the angle β, γ between local axises (23a, 23b).

Therefore, the easiest coordination of Coriolis's forces can be achieved in case of establishing all local axises 23, 23a, 23b on equal angular distances from each other (cx=β=γ) in the plane 29 around the precession axis 26. In the same way, the easier coordination of Coriolis's forces can be achieved in case of establishing all working solids 42, 42a, 42bc on identical distances 31,31a,31b i.e. A=B=C.

AU above mentioned steps of coordinating motion conditions ω, ω; geometrical parameters A and D and masses M of working solids 42, 42b, 42b provide the levitation force 3F _k without vibrations of such a gyroscopic system in FIG.7.

I have discovered that the above mentioned balance of both energies (Ei _|| (ω), E _LL OO) exists in the nuclear structure of the atom, where synchronization of angular

rotational frequency ω (spin) with the angular precession velocity ω of the nucleons exists, providing the ratio i= ω/ω, where i - is an integer that is equal to the quantity N of nucleons.

If to take into account that V/A=V _a /B =Vι,/C=ω and ω=Nω, where N is an integer that is equal to the quantity of working objects in FIG.7 we are able to provide movement conditions for working objects with the above mentioned balance of inertial energies E _i(| (ω), E _L L(ω).

It can be considered as an inertial forces resonance (IFR) taking place in nuclear structure of the atom, which is also a cause of the existence of gravitation.

The above mentioned mass distribution law nii=f(Ai) can be provided by respective configuration of the outer surface of the said working object 42 in FIG.7 along the local axis 23 in respect to the conic surface 47a.

The mass distribution law can be provided also by respective configuration of the inner surface of the said working ring 43 in FIG.5 along the local axis 23 in respect to the conic surface 47 while the outer surface of the said working ring 43 is cylinder-shaped.

I have discovered that utilizing as the said working object 42 in FIG.7 a part of a hollow cone allows to reduce the total weight of such a gyroscopic system by 30%-40%. In FIG.8 a gyroscopic system is shown for comparison against the known gyroscopic apparatus in FIG.3. The offered working solid 50 (50a) is a part of a hollow cone 47. The apex 51 of the cone 47 is focused in the direction of the precession axis 26. The said working cone 50 in FIG.8 is rotated in a direction C with the angular frequency ω around the local axis 23. Working cone 50, having the base diameter 25, is supported by a portable shaft 44. The said portable shaft 44 is unmovablely connected to the vertical shaft 52. Working cone 50 is moved around the vertical axis 26 (Z) with respective precessional velocity V along a circular trajectory 28 disposed in the plane 29.

The forced precession of the said rotated working cone 50 around the axis 26 is supplemented by a forced precession of the additional working cone 50a quantified by angular rotational frequency ω _a . The distance from a mass point 33a of working cone

50a up to the axis 26 is designated as B (B^A) in FIG.8. The said working cone 50a

having a base diameter 2R _a , moves around the same precession axis 26 with precessional velocity V _a simultaneously with rotation around the rigid portable shaft 44a unmovablely connected to the said vertical shaft 52. The said working cone 50a is moved by precession force along the circular trajectory 28a that is allocated in the same plane 29.

The opposite established working cone 50a has rotating direction G which is defined by the above mentioned specifying rule according to which it is necessary to tilt conditionally the vector ω (37) of the forced precession (that is directed vertically upwards in FIG.8) around the point 38 of the intersection of axises 23 and 26 to combine 0 with the local axis 23a along a trajectory 39 and the direction 40 of the rotational vector αζ has to coincide with the direction 41 of the tilted vector ω' (the intermediate position of the vector ω' is shown in FIG.8 as a dotted arrow).

As a result, the rotational direction G of the said working cone 50a is directed opposite the rotational direction C of the said working cone 50 as in the above mentioned gyroscopic apparatus in FIG. 3.

If to apply the Zhukovsky's rule to motion conditions of the additional working cone 50a it will be possible to define the direction of an additional Coriolis's force F _ka that acts upon the mass of the said working cone 50a upwards. _Q The numerical value of the force Fi ₅₃ can be calculated according to (1) .

As it is clearly visible in FIG.8, there is a pair of two-axises rotated working masses (cones) 50, 50a similar to the known gyroscopic apparatus in FIG.3 but having the rigid common portable shaft 44 (44a) unmovablely connected to the vertical shaft 52, that provides the precession of both working cones 50, 50a along circular trajectories 28, 5 28a, disposing in the common plane 29. Two continuous forces F _k and F^ are acting coordinated in one direction along the precession axis 26 and they can move both rotating cones 50, 50a with a total force F _k + Fi _∞ without vibrations.

As the said working object 20 in FIG. 4 any mass can be utilized with a big _Q densities. Therefore it would be preferable to utilize a fluid, which can be transferred around the local axis in a ring-shaped transferring means (in a tube or in a pipe).

The offered method of utilizing working fluid as the said working object 20 is shown in FIGs.9,10. There is a top view in FIG.9 of the said working fluid 53 which is transferred around the local axis 23 simultaneously with forced precession around the precession axis 26 with angular velocity ω. The distance from a mass point 33 of the said working fluid 53 up to the precession axis 26 is designated as A in FIG.9.

In FIG.10 a view of the section along a line G-G according to FIG.9 is shown. The said working fluid 53 has toroidal configuration with an outer diameter D and with an inner diameter d. Working fluid 53 in FIGs.9,10 is uniformly allocated in a plane 54 around the local axis 23 and forms a separate fluid cycle 55. The precession velocity V of the said fluid cycle 55 is defined as the product of the distance A (31) and of the angular precessional velocity ω as follows: V=Aω.

The plane 54 in FIG.9 is inclined with respect to the velocity vector V of the forced precession at an angle φφnll which can be chosen from the range -60°<φ< 60°.

In FIG.9 the angle φ is equal to 45°. Working fluid 53 is moved by a transfer means (is not shown) along the secondary circular trajectory 56 (FIG.10) with linear velocity V _f . The width b in FIG.9 of the toroidal fluid 53 can be defined as b=(D-d)/2. The mass of the toroidal fluid cycle 55 is numeric quantified by a value M _f which is determined by its outer D and inner d diameters as follows:

Mf=0.25π ² (D-d)(D ² -d ² )s where s -is the density of the said working fluid 53.

The transfer of the toroidal fluid 53 along the secondary circular trajectory 56 can be considered as rotation of the said working fluid, having mass M ₆ around the said local axis 23 with the respective angular frequency ω.

Therefore the Coriolis's Force F _k generated by toroidal fluid cycle 55 can be defined according to (1) as

F _k = M _f ωV sin(π/2-φ).

The heaviest fluid is known to be the mercury, density s of which is more than 13.5gr/cm ³ . Such a working liquid can be transferred in a pipe by an electromagnetic pump to provide the transfer along the circular trajectory 56 for a big Coriolis's force by small dimensions of such a gyroscopic system.

For example, at D=12cm, d=8cm; V=10m/seα; ω = 600min-l; s=13.5*10 ³ kg/m ³ ; A= 10cm the Corioli's force is appearing, achieving the value of

F _k = 1 287N.

If to utilize a lot of cycles 55 of the toroidal working fluid 53 the total value of the plurality of Coriolis's unidirectional forces has to increase and the offered method allows to utilize a big quantity of cycles 55 of the working fluid 53 which are allocated around 5 the precession axis 26 as it is shown in FIG.9 in dotted lines.

The inclination of the secondary motion trajectory 56, lying in the plane 54, with respect to the velocity vector V allows to achieve maximum establishing density of fluid cycles 55 around the precession axis 26. For example, in FIG.9 thirty additional fluid cycles 55 are shown in dotted lines. 2 _Q The maximum quantity N _m of cycles 55 can be determined as follows:

N _m =int(2πA/b)= int(2πA/(D-d)/2).

For the above mentioned example in FIG.9 the quantity of fluid cycles 55 is defined as follows: N _m =int(4π0.1/(0.12-0.08))=62.8/2=31.

As the charged particles have some mass I offer to utilize plasma (charged 15 particles) as the said working fluid 53 to be transferred around the local axis in a wire or in a tube by an electromagnetic field with a big transfer velocity V _f > lOOm/sec.

The curved secondary trajectory 56 in FIG.10 of the fluid motion around the local axis 23 can be not only a circular trajectory as an exclusive motion kind of the said working fluid 53. Therefore, in the same way in FIG 11 working fluid 57 in a form of charged particles of plasma can be transfered around the local axis 23 along the secondary elliptic trajectory 58 (FIG.ll) to increase the levitation force of the Coriolis's effect. The top view of the FIG.ll is the same as it is shown in FIG.9.

In this case the above mentioned width b of charged particles 57 in FIG.ll can be decreased to some tenth of a millimetre (b=0.2mm) and the quantity N _m of fluid cycles

58 is determined as

25

N _m = int(2πA/b)=6.28*0.1m/0.0002m= 3140.

Such a quantity (3140) of fluid cycles 58 would have a view of a plasma sphere

59 with a diameter 5-20cm, rotating around the precession axis 26 as it is shown in FIG.12.

There is plurality of cycles 58 of charged particles in FIG.12. One of cycles 58 is on shown in FIG.12 allocated in the plane 54 (hatched in FIG.12).

In the nature such a plasma sphere 59 shown in FIG.12, exists in the form of a fireball and presence of its rotation around the precession axis 26 explains an opportunity

of lag of the fireball above the surface or its movement to any direction even against the wind under action of the Coriolis's forces.

The offered method of generating Coriolis's forces can be explained on the basis

5 of the diagram in FIG.13 illustrating the working principle of the offered gyroscopic system 60 as well.

Base reference numerals will be used in the embodiment of FIG.13 as they have been shown in the description according to FIG.7.

The offered gyroscopic system 60 in FIG.13 comprises a transport platform 61,

10 an engine 62 established on the said transport platform 61; working solids 63, rotating around respective separate local axises 23 by plurality of drive means 64, simultaneously with forced precession around the precession axis 26 provided by a precession unit 65 for supporting and moving the said working solids 63 along the circular precessional trajectory 28 allocated on the conic surface 47a around the precession axis 26. Each of

, c the said drive means 64 is an electric motor.

The gyroscopic system in FIG.13 is provided by a synchronizing means 66, which is established near the working solid 63. Working solid 63 is conic-shaped, having a maximum outer diameter D defined as D= kAω/ω, where A - is a distance 31 from the mass point 33 of the said working solid 63 up to the said precession axis 26; ω - is

2« angular rotation frequency of the said working solid 63, ω - is angular precessional velocity of the said working solid 63 around the precession axis 26; k>2 is a dimensionless factor. Working solid 63 is apart of the cone 47, having an apex 51.

Synchronizing means 66 in FIG.14 comprises the first tachometer 67 to measure the said angular precessional velocity ω; the second tachometer 68 to measure the said

^_ rotational angular frequency ω; a controller unit 69 to regulate rotation frequency of the said separate electric motor 64 by an electronic switch 70 that connects periodically power supply 71 to the separate electric motor 64 (drive means). The quantity of the said synchronizing means 66 in FIG.13 is equal to the quantity of the said working solids 63. The precession unit 65 in FIG.13 can be manufactured in a form of a star-shaped rigid structure with five vertexes 72. The precession unit 65 carries odd number (five) of working solids 63 rotated around respective local axises 23. Working solids 63 are established on the said precession unit 65 at the ends of star vertexes 72 above the said platform 61 with the rotation possibility around the respective local axis 23. Working

solids 63 have the possibility to move together with the said precession unit 65 around the precession axis 26 by the said engine 62 established on the said platform 61. Output shaft 73 of the engine 62 is directed along the axis 26 disposed outside all working solids 63. This shaft 73 is connected to the precession unit 65 to rotate it around the precession axis 26.

Preferably, all working solids 63 are disposed on equal distances A from the common precession axis 26.

The gaseous environment in FIG.13 around the precession unit 65 creates the resistance with respect to the precessional movement of the said working solids 63 I _Q around the precession axis 26, decreasing the transforming efficiency of the driving torque on the output shaft 73 of the engine 62 into the Coriolis's forces.

Therefore, the precession unit 65 is established in the rarefied gaseous environment 74 or in vacuum to decrease the resistance of the enviroment 74 against the precessional motion of working solids 63.

15

The gyroscopic system 60 in Fig. 13 operates as follows:

Power into the engine 62 causes rotation of the output shaft 73 together with the precession unit 65. The rotation of the said working solid 63 around the respective local axis 23 with angular frequency ω is provided by separate electric motor 64 established on the precession unit 65. The rotation of the precession unit 65 provides the forced movement of all working solids 63 around the precession axis 26 with angular velocity ω.

The tachometer 67 (FIG.14) of synchronizing means 66 provides the measurement of the said angular precessional velocity ω. The tachometer 68 of synchronizing means 66 provides the measurement of the said angular frequence ω of the rotation of working solid 63. The controller unit 69 compares data of both tachometers 67, 68, forming output impulses with frequence F depending on the result of the calculation N=ω/ω. In the offered embodiment the angular frequency ω of each working solid 63 is synchronized with the angular precessional velocity ω of the output shaft 73, providing a ratio ω/ω =N, where N is an integer, that is equal to the quantity of working solids 63 (in FIG. 13 the ratio N=5).

Output impulses of the controller unit 69 are activating periodically the electronic switch 70 that connects power supply 71 to the separate electric motor 64 with a

frequence F. If the result N of calculation is more than 5 (the number 5 is equal to the quantity of working solids 63) the controller unit 69 is changing the frequence F to be lower and the average value of the current from the power supply 71 is decreasing. As a result, the rotation frequence ω of the separate electric motor 64 will be equal to 5ω as well as the rotation frequence ω of the respective working solid 63. If the result N of calculation is less than 5 the controller unit 69 is increasing the frequence F and the average value of the current from the power supply 71 is increasing.

As a result, the rotation frequence ω of the separate electric motor 64 will be also equal to 5*ω as well as the rotation frequence ω of the respective working solid 63. The coordination of the angular rotational frequency ω with angular precessional velocity ω provides balance of the rotational angular energy E _|| (ω) of each working solid 63 with the angular energy Ej_(ω) of the precession of the same working solid 63.

Synchronizing means 66 provides also rotation of the respective working solid 63 around respective local axis 23 in the direction that is coordinated with the direction of the forced precession according to the offered specifying rule.

If to apply the offered specifying rule (along a trajectory 39) to each working solid 63 - all rotational vectors ω will be directed outside with respect to the precession axis 26 i.e. all vectors ω should have a centrifugal directions as it is shown in FIG.13.

Motion conditions of working solids 63 provide appearing of Coriolis's forces F _k that are acting upon masses of working solids 63 unidirectionally and continuously along the axis 26 according to the Zhukovsky's rule. As it is clearly wisible in FIG.13 five

Coriolis's forces F _k are directed upwards along the axis 26 in the offered gyroscopic system 60.

Hence, the offered gyroscopic system 60 in FIG.13 is able to transform the driving torque on the output shaft 73 of the engine 62 in the plurality of Coriolis's unidirectional forces F _k that have continuous and uniform properties.

These Coriolis's forces are acting upwards upon the solids 63 providing the levitation of precession unit 65 together with the transport platform 61 that is connected to the engine 62 and to the precession unit 65 by the output shaft 73. On the transport platform 61 a cargo 75 can be established which is necessary to lift, for example, into circumterraneous orbit.

The forced precession of the plurality of working solids 63 around the precession axis 26 is a cause for reaction torque T _n which should overcome the engine 62 by its

output torque on the output shaft 73. The numerical value of the reaction torque T ₁ . can be defined as T _r = qNF _k *A where N is the quantity of working solids 63; q - is a dimensionless factor.

As a result, the transport platform 61 will rotate itself during the levitation process in the opposite direction relatively to the direction of the forced precession of working solids 63. The angular rotational velocity ω _r (76) of the transport platform 61 depends on many things: mass of the platform 61, platform size, weight of the cargo 75, distributions of the cargo 75 on the platform 61, etc.

The rotation of the transport platform 61 around the axis 26 is not an important thing for the cargo 75 during such a levitation, but for equipage member 77 that would be present on the transport platform 61, such a rotation is an uncomfortable condition, especially if the angular velocity ω _r of the rotation of the transport platform 61 is more than O.lmin ^"1 .

Therefore I offer an improvement of the method illustrated in FIG.15 that consists in utilizing even number of rotated working objects 20, 20a (for example, sixteenth working objects in FIG.15); in distributing all working objects at least into two groups, for example, the first group 78-78 comprises eight working objects 20 and the second group 79-79 comprises eight working objects 20a. The first group 78-78 of rotated working objects 20 is moved around the precession axis 26 clockwise; the second group 79-79 of rotated working objects 20a is moved around the same axis 26 counterclockwise.

Here the above mentioned reaction torque T _r = q8F _k *A is caused by the forced precession of the first group 78-78 of working objects 20. This reaction torque T ₁ . is counterbalanced by reaction torque -T _r = q8F _k *B of the forced precession of the second group 79-79 of working objects 20a.

Motion conditions of the first group 78-78 of working objects 20 are the same as they are in the embodiment that it is described on the basis of FIG.13.

For defining rotational directions of the second group 79-79 of working objects 20a the offered specifying rule is applied.

The vector -ω (37a) of the forced precession (that is directed vertically downwards in FIG.15) is conditionally tilted according to the offered specifying rule around the point 38a of the intersection of axises 23a and 26 along a trajectory 39 to

combine with respective local axis 23a and the direction 40 of the vector ω has to coincide with the direction 41 of a tilted vector ω' of the forced precession.

If to apply the offered specifying rule to each local axis 23a, the respective rotational vector ^" ωOf each object 20a would be directed inside to the precession axis 26, 5 i.e. all vectors ^" αTshould have a centripetal direction as it is shown in FIG.15.

Precession unit 65 in FIG.13 can be also embodied in a form of a pair of flat rigid disks, disposing perpendicularly to the precession axis 26, and a plurality of supporting frames to provide the orientation of working solids along respective local axises.

10 FIG.s 16 and 17 illustrate the second preferable embodiment of the gyroscopic system 80. As the said working solid can be utilized a flywheel with conic inner surface.

Some reference numerals will be used in the embodiment of FIGs 16 and 17 as they have been shown in the description of the gyroscopic system according to FIG.13. As working solids three flywheels are utilized in a form of a thin-walled rotor with conic . - inner surface.

Gyroscopic system 80 in FIGs 16,17 comprises a casing 81, an engine 82, three flywheels 83 with conic inner surface, bevel cogwheels 84, connected to respective flywheels 83, a precession unit 85-85 in a form of a pair of disks 86, 87 for supporting and moving flywheels 83 around the precession axis 26 by supporting frames 88. AU flywheels 83 have identical configuration and mass. All bevel cogwheels 84 have the same teeth quantity K.

Local axises 23 in FIG.16 are inclined with respect to the precession axis 26 at the angle ψ that is equal to 91°. The precession unit 85-85 is provided by separate supporting frames 88 in which flywheels 83 are disposed with rotation possibility around the respective local axises 23. Disks 86, 87 of the precession unit 85 are connected by

25 frames 86 which play a role of distance elements, providing the rigidity of the precession unit 85. The axis 26 of the forced precession is disposed outside flywheels 83. The precession unit 85 may be connected directly to the output shaft 89 of the engine 82. Flywheels 83 are ldnematical connected to the casing 81 by a central bevel cogwheel 90 which provides together with respective cogwheel 84 rotational synchronization of each ^Jυ flywheel 83. The central bevel cogwheel 90 has a quantity L of its teeth. The precession unit 85 is established on a bearing 91 to provide its rotation around the precession axis

26. Each flywheel 83 is established on respective shaft 92 that is rotated together with respective flywheel 83 in bearings 93 placed in separate respective supporting frame 88.

Each flywheel 83 has a diameter D defined as D=Aω/αW2/(l +f), where A is a distance from the mass point 33 of the respective flywheel 83 up to the precession axis 26; ω - is the angular rotation frequency of the flywheel 83, ω - is the angular precessional velocity of the precession unit with respect to the axis 26; f=d/D; d - is an internal diameter 49 of the flywheel 83.

The casing 81 of the gyroscopic system 80 is fixed to the transport means 94 (spacecraft) by plurality of the respective fixing elements. The pair of bevel toothed gears 84, 90 forms a bevel gear transmission having a transmitting ratio i that is equal to an integer defined as i=L/K where L- is the teeth quantity of the central cogwheel 90, K - is the teeth quantity of the cogwheel 84. In this embodiment the ratio i is equal to 3.

The bevel gear transmission 84, 90 executes a function of a synchronizing unit, providing balance of the rotational angular energy Ey(ω) of each flywheel 83 with the angular energy Ej_(ω) of the precession of the same flywheel 83.

All local axises 23 are disposed on equal angular distances (120°) from each other in the plane A-A in FIG.16 around the precession axis 26.

Between the casing 81 and transport means 94 a sealant means 95 is established. From the internal space 96 of the gyroscopic system 80 air is removed. The sealant means 95 provides the defined level of vacuum. Presence of vacuum in the internal space

96 provides lower resistance against the motion of flywheels 83 around the precession axis 26 and it increases efficiency of the gyroscopic system 80.

Supporting frame 88 contains near each flywheel 83 a displacement means 97 providing a shift of the flywheel 83 along the respective local axis 23 to change the radius of the motion trajectory 28 around the axis 26 in FIG.17.

The displacement means 97 in the simplest case in FIG.16 is the spring. The flywheel 83 is coupled to the shaft 92 by a sliding coupling 98.

The gyroscopic system 80 in FIG.s 16,17 operates as follows: Power into the engine 82 causes the its output shaft 89 to rotate together with the precession unit 85. Rotation of the precession unit 85 provides the forced movement of flywheels 83 around the precession axis 26 with an angular velocity ω. Simultaneously,

the bevel cogwheel 84 rotates together with the respective flywheel 83 because it (cogwheel 84) is rolling under the motionless central cogwheel 90 which is connected to the casing 81, for example, by the plurality of screws. The angular frequence ω of the rotation of the flywheel 83 is defined by the angular velocity ω and by the transmitting ratio i of the gear transmission 84,90 as follows: ω=iω.

The direction J of the rotation of the flywheel 83 is defined by the position of the cogwheel 84 with respect to the central cogwheel 90, namely the cogwheel 84 has to be located under the central cogwheel 90 to provide the performance of the above mentioned specifying rule, according to which all rotational vectors ω of flywheels 83 should have centrifugal directions.

The precession velocity V of the flywheel 83 is defined by the angular precessional velocity ω and by the distance 31 (A) of the flywheel 83 up to the precession axis 26 as follows: V=Aω.

Motion conditions of flywheels 83 provide appearing of Coriolis's forces F _k that are acting unidirectionally and continuously along the axis 26 according to the Zhukovsky's rule. There are three Coriolis's forces F _k in FIG.16 which are acting upwards along the axis 26 in the offered gyroscopic system 80.

The total levitation force F _t generated by the gyroscopic system 80 is defined by the following equation: F _t =2NMωV if to take into account the equation (1) and the fact that N is a quantity of flywheels 83; M - is the mass of the flywheel 83. If to take into account the known equality V=Aω the expression can be written as

F _t = 2NMωωA. (9)

If to take into account that ω=iω and i= N we can finally receive

F _t = 2MAω ² i ² (10) where N=3 is the quantity of flywheels 83; M - mass of the flywheel 83; ω - is the rotational frequency of the output shaft 89.

In fact, the factor 2 in the above given equation (10) takes place under conditions of perfect balance of the rotational angular energy Ey(ω) of each flywheel 83 and the precessional angular energy Ej_(ω) of the same flywheel 83.

In practice the equation (10) has a little bit another structure, namely F _t = kMAω ² i ² (11)

where 0.5 < k < 2 depending on the balance accuracy of the above mentioned energies Ey(ω) and Ej _. (ω) of the flywheel 83.

As it appears from the equation (11) the total levitation force F _t generated by the gyroscopic system 80 is proportional to the square of the rotation frequency ω of the engine output shaft 89.

The displacement unit 97 works to linearise the dependence (11) by influence on the above mentioned factor k. The displacement unit 97 contains a spring that pushes the flywheel 83 toward the precession axis 26 to establish it in the most inner position which is shown in FIG.16. At such a position of the flywheel 83 the factor k is approximately equal to 2 thanks to provide the perfect balance of the above given energies E _j| (ω) and Ej_(ω) of the rotating and precessing flywheel 83.

If the angular velocity ω of the output shaft 89 is increased therefore a centrifugal force increases as well and flywheel 83 is changing its position on the shaft 92 under the action of the centrifugal force. The intermediate position of the flywheel 83 is shown in

FIG.16 in dotted lines as a position 99. At the position 99 the balance accuracy of the above given energies E _| |(ω) and Ej_(ω) of the flywheel 83 is decreased and the factor k falls to 1. The dependence of the factor k on the angular velocity ω can be written as k=2/(ω+l). As a result, the equation (11), describing the total levitation force F _t will have a more linear structure, namely F _t = 2NMAωi ² .

Other possibilities of changing the motion trajectory 28 of flywheels 83 are connected to more complicated hardware and software of the displacement means 97.

FIGs 18 and 19 illustrate the next embodiment of the gyro-turbine 100 that comprises a casing 81, two electric engines 82, 82a, four hollow working cones

50,50a,50b,50c bevel cogwheels 84, connected to respective working cone 50 (...5Oc), a precession unit 85-85 in a form of a pair of disks 86, 87 for supporting and moving working cones 50...5Oc around the precession axis 26. All bevel cogwheels 84 have the same teeth quantity K. All working cones 50 have identical configuration and mass. Each local axis 23 in FIG.18 is disposed with respect to the precession axis 26 under an angle ψ, that is defined as: The precession unit 85 is provided by supporting elements 101, 102 in which cones 50...5Oc are established with

rotating possibility around the respective local axis 23. The axis 26 of the forced precession is disposed outside working cones 50...5Oc. Working cones 50...5Oc are kinematical coupled to the top part 103 of the casing 81 by a bevel central cogwheel 90 which provides together with respective cogwheel 84 rotational synchronization of each working cone 50...5Oc. The central bevel cogwheel 90 has quantity L (L>K) of its teeth. The top disk 86 of the precession unit 85 is established in bearings 104, 105 with the rotation possibility around the axis 26. At least two opposite working cones 50 and 50a are established on respective output shafts 89 of engines 82, 82a. Working cones 50 have the possibility to rotate in bearings 93,106 which are established in separate supporting elements 101, 102.

The pair of cogged gears 84, 90 forms a bevel gear transmission 107 (FIG.19), having a transmitting ratio i that is equal to an integer defined as i=L/K = 4 where L- is the teeth quantity of the central cogwheel 90, K - is the teeth quantity of the cogwheel 84. The bevel gear transmission 107 executes a function of a synchronizing unit providing the said balance of the rotational angular energy E _|| (ω) of each working cone 50 with the angular energy Ej_(ω) of the precession of the same cones 50.

Each working cone 50 ...50c has identical configuration and a size of its base diameter D - 25, which is defined as D= kUω/ω, where U (FIG.19) - is the distance 108 from the respective cone's base 109 up to the precession axis 26; ω - is angular rotation frequency of working cone 50, ω - is angular precessional velocity of the said working cone 50 around the axis 26; k - is a dimensionless factor that has been chosen from a range 2 < k < 7.

The casing 81 of the gyro-turbine 100 can be fixed to the transport device 94 (spacecraft) by plurality of respective fixing elements 110.

Electric engines 82, 82a are installed inside the respective hollow working cone 50 (50a). Another pair of working cones 50b, 50c may be the same as cones 50, 50a but without electric motors inside. Working cone 50b (50c) is established on the shaft 111. Both disks 86 and 87 of the precession unit 85 are coupled by distance elements 112, fixing elements 113 and by edges 114 (FIG.19) which provide the rigidity of the precession unit 85.

Two electric motors 82, 82a are disposed opposite each other in FIG.18. All working cones 50 pass through trapeze-shaped openings 115 of the bottom disk 87 of the precession unit 85. One of the said openings 115 is shown completely in FIG.19 as if it would be provided in the top disk 86. Such an embodiment allows to decrease the size of the offered gyro-turbine along the axis 26 in FIG.18. Electric motors 82, 82a can be connected to the power cable 116 by slip ring 117 and electric brushes 118.

Sealant means 95 in FIG.18 is established between the casing 81 and its top part

103, providing the possibility to create the rarefied gaseous enviroment inside the casing

81. From internal space 96 of the casing 81 air is removed to provide the defined level of vacuum for decreasing the resistance of the air against the precession movement of working cones 50 during the forces precession.

The gyro-turbine 100 in FIG.s 18,19 operates as follows:

Power into the electric motors 82 causes their output shafts 89 to rotate together with respective working cones 50 and cogwheels 84 with rotational angular frequency ω. The rotation of the bevel cogwheel 84 provides the forced movement of precession unit 85 around the precession axis 26 with an angular velocity ω because the cogwheel 84 is rolling under a motionless central cogwheel 90 which is connected to the top casing part 103 by the plurality of screws 119. The angular velocity ω of the rotation of precession unit 85 is defined by the angular frequency ω and by the transmitting ratio i of the gear transmission 84, 90 as follows: ω=ω/i.

The direction J in FIG.19 of the rotation of precession unit 85 is defined by the position of the cogwheel 84 with respect to the central cogwheel 90, namely the cogwheel 84 has to be located under the central cogwheel 90 to provide the performance of the above mentioned specifying rule, according to which all rotational vectors ω of working cones 50 should have centrifugal directions as it is shown in FIG.19.

The precessional velocity V along the circular trajectory 28 of working cones 50 is defined by the angular precessional velocity ω and by the distance 31 (A) from the mass point 33 of working cone 50 up to the precession axis 26 as follows: V=Aω.

Motion conditions of working cones 50 provide appearing of Coriolis's forces F _k that are acting unidirectionally and continuously along the axis 26 according to the Zhukovsky's rule. There are plurality of Coriolis's forces F _k in FIG.19 which are acting

upwards along the axis 26 upon masses of working cones 50...5Oc in the offered gyro- turbine 100.

The total Coriolis's force F _t generated by gyro-turbine 100 is defined by the above mentioned equation (11): F _t =2MAω ² i ² . Both motors 82 of the gyro-turbine 100 have to overcome a torque reaction T ₁ . on the shaft 89. The torque reaction of the gyro-turbine 100 tries to turn the transport device 94 in the direction that is opposite to the rotation direction of the precession unit 85. The counterbalance of the torque reacton T _r can be provided by establishing the second gyro- turbine 100a beside in one plane as it is shown in FIG.19. The precession unit 85 of the

10 gyro-turbine 100a is rotated in the opposite direction relative to the precession unit 85 of the gyro-turbine 100.

As the precession unit we can also utilize a pair of carriers and plurality of portable shafts disposed along the respective local axises 23 around the precession axis , r 26. Special established carriers allow to reduce a torque reaction of the gyro-turbine to zero.

FIGs 20 and 21 illustrate the third preferable embodiment of the gyro-turbine 120. Some reference numerals will be used in the embodiment of FIGs 20, 21 as they have been shown in the description of the gyro-turbine according to FIG.18. As working solids six working cone are utilized in the offered gyro-turbine 120.

The gyro-turbine 120 in FIG.20 comprises a casing 81, an engine 82, six hollow working cones 50, 50a, helical cogwheels 121 connected to respective working cones 50, 50a in its most outer base; a precession unit 85 in a form of a pair of carriers 122, 123 and six portable shafts 44, 44a.

Portable shafts 44, 44a provide supporting and moving of working cones 50 along 5 a precessional trajectory 28 around the precession axis 26. All working cones 50 have identical size and mass. All helical cogwheels 121 have the same teeth quantity K.

Working cones 50 are distributed onto two groups, namely the first group 78-78 includes three working cones 50; the second group 79-79 also includes three working cones 50a.

30 The first group 78 of working cones 50 is established on respective portable shafts

44, fixing by one end in the first carrier 122 at pivot points by pins 124.

The second group 79 of working cones 50a is established on respective portable shafts 44a also fixed by one end in the second carrier 123 at pivot points by pins 124a.

Each local axis 23 is disposed with respect to the precession axis 26 at the angle ψ which is chosen from a range 95°- 135°. Working cones 50 (50a) are established in 5 bearings 93 with rotation possibility around the respective local axises 23. Carriers 122,

123 are established in bearings 125 with the rotation possibility around the precession axis 26. The axis 26 of the forced precession is disposed outside of working cones 50.

Working cones 50a are kinematical coupled to the top part 81a of the casing by a helical cogged ring 126a which provides together with respective cogwheel 121 a rotational 10 synchronization of each working cone 50a. Working cones 50 are kinematical coupled to the bottom part 81 of the casing by a helical cogged ring 126. The helical cogged ring

126 (126a) has a quantity L of its teeth.

The pair of helical toothed gears 121, 126 forms a helical gear transmission 127 having an integer transmitting ratio i which is equal to the quantity of working cones 50 25 in the respective group defined as i=L/K = 3; where L - is the teeth quantity of the cogged ring 126, K - is the teeth quantity of the cogwheel 121. AU working cones 50,

50a have identical mass and sizes.

Each working cone 50 has a base diameter D 25 defined as D= kU/i (FIG.21), where U is the distance from the respective cone base 109 up to the precession axis 26; i 20 - is the above mentioned transmitting ratio; k - is a dimensionless factor that has been chosen as 2.1 < k < 5.

The casing 81, 81a of the gyro-turbine 120 is fixed by plurality of respective fixing elements 110. The gyro-turbine 120 is established in the transport means 94

(spacecraft). r _y e The helical gear transmission 127 executes a function of a mechanical synchronizing unit, providing balance of the rotational angular energy Ey(ω) of each working cone 50(5Oa) with the angular energy Ej_(ω) of the precession of the same working cone 50 (50a).

The electric motor 82 is established between the respective carriers 122, 123. Two 30 carriers 122, 123 are allocated around the common precession axis 26. Such an improvement provides the offered method of counterbalancing the torque reaction which has been illustrated in FIG.15. The electric motor 82 can be connected directly to the power cable 116.

The output shaft 89 of the electric motor 82 passes through. The bottom end 89 of the output shaft is coupled to the bottom carier 122; the top end 89a of the output shaft is connected to the gear box 128. The gear box 128 provides a transmitting ratio -1 at which the output shaft 129 of the gear box 128 rotates in the opposite direction with

5 respect to the rotation direction of the output shaft 89a of the engine 82 with the same angular velocity ω. The casing of the motor 82 is coupled to the casing 81 of the gyro- turbine 120. The same is true for the casing of the gear box 128.

Sealant means 95 is allocated between the top part 81a and bottom part 81 of the casing. From internal space 96 of the gyro-turbine 120 air is removed, providing the

10 defined level of vacuum to decrease the resistance of the air against the precession movement of working cones 50.

The gyro-turbine 120 in FIG.20 operates as follows:

Power of the output shaft 89 of the engine 82 in FIG.20 causes to rotate the whole

15 assembly of the carrier 122 together with precession shafts 44, working cones 50 and respective helical cogwheels 121 clockwise. Simultaneously at the forced precession of working cones 50 cogwheels 121 are rolling below the cogged ring 126 that is connected to the casing 81. In the same way the output shaft 129 of the gear box 129 causes to rotate the whole assembly of the carrier 123 together with portable shafts 44a, working

_ _ cones 50a and respective helical cogwheels 121 counterclockwise. Simultaneously at the forced precession of working cones 50a cogwheels 121 are rolling below the cogged ring

126a connected to the top part 81a of the casing.

Cogwheels 121 and cogged ring 126 (126a) provide the synchronization of the rotational angular frequency ω of working cones 50, 50a around local axises 23 with the precessional angular velocity ω of working cones 50, 50a around the axis 26.

The rotational angular frequency ω of working cones 50, 50a is defined as ω=i*ω, where i -is the transmitting ratio of the gears 121,126; ω- rotational angular velocity of the output shaft 89 of the motor 82. The transmitting ratio i can be defined as i=M/L where M - is the tooth quantity of the central cogged ring 126; L- is tooth quantity of each cogwheel 121. Three working cones 50, 50a are precessing in the plane C-C in FIG. 20 around the axis 26 similar to the diagram shown in FIG.15.

W 2

Motion of working cones 50, 50a in FIG.20 generate plurality unidirectional

Coriolis's forces F _k , which are focused in the direction of the axis 26 and these forces are acting uniformly and continuously (not pulsatively) upon the casing 81 and upon the spacecraft 94 to provide the plane-parallel continuous motion in the determined direction.

The offered invention can be utilized in many branches of transport technology. Except space technologies, such gyro-turbines can be used in a daily life to remove traffic jams from city roads. It is enough to establish four gyro-turbines illustrated in FIG.18 in a car to lift this car above the city road and to evacuate the car from the traffic jam. Two offered gyro-turbines can be utilized in sport by developing a soaring board, that is able to be floating together with a sportsman above the ground on a height from 0.5cm to 1 metre. The method presented here allows to create, for example, a silent submarine which can dive without of filling ballast tanks by water. Such a submarine is able to fly up if necessary in any height.