METHOD AND DEVICE FOR CREATION AND CONTROL OF GRAVITATIONAL ACCELERATION

TECHNICAL FIELD

The invention refers to a method and device for creation and control of gravitational acceleration, which will find application for stopping, driving and manoeuvring of simulators, test stands, and vehicles in case of removed mechanical connection between engine and support. The invention will be mainly used for vehicles in a medium that restricts or excludes the connection between engine and support - the outer space.

PRECEDING STATE OF THE TECHNIQUES Unknown method and device for creation and control of gravitational acceleration.

INVENTION TECHNICAL ESSENCE

The essence of the invention involves a method for creation and control of gravitational acceleration, which is accomplished by means of a constant force impact of centrifugal nature of at least two operating bodies on a free main body. The operating bodies exercise forced antiphase circular motions. These circular motions are ensured by and are proportional to the intensity of a synchronous inhomogeneous rotating mechanical field. The field is generated by a resonance frequency modulation of a uniform rotary motion applying the kinematic and frequency parameters of a harmonic vibratory field. The frequency of the uniform rotary motion is equal to the resonance frequency of the vibratory field. The transverse force components are mutually nullified. The principal vector of the external lateral forces changes periodically. It is a sum of all impacts of all operating bodies and it has mean integral value different form zero in a controlled direction. The principal vector of the external lateral forces is applied to the mass centre of the system "main body - operating bodies". It changes the system momentum in the controlled direction and transfers normal acceleration to the system. Fixing the direction of the principal vector of the external lateral forces to the main body means permanent time overlapping (coincidence) of the dynamic direction with the designed (controlled) direction in the impact plane. It is accomplished only once by means of mutual stepless time dephasing between the kinematic parameters of the homogeneous rotating field and harmonic vibratory field. The direction control of the principal vector of the external lateral forces is achieved by dephasing the fixed direction with regard to the direction of movement of the main body and the magnitude control is achieved by changing the modulation depth as a function of the stepless control of the magnitude of the resonance amplitude of the vibratory field.

The essence of the invention also relates to a direction control of the principal vector of the external lateral forces, which is accomplished, too, by dephased fixing of the dynamic direction with regard to the designed direction at ±^ rad,

while the magnitude control is achieved by means of constant mutual stepless time dephasing of the kinematic parameters of the homogeneous rotating field and the harmonic vibratory field.

An advantage of the method, in compliance with the invention, is the possibility under the conditions of removed mechanical connection between engine and support or in a medium, restricting or excluding such a connection, to achieve an accelerated motion of a material macro-object without a change in its mass. The essence of the invention also includes a device for creation and control of gravitational acceleration, which is built by attaching a hollow central axle to the mass centre of the main body. On the central axle sequentially and freely supported by bearings in their mass centres are: a phase synchronizer, a linear amplitude amplifier, a harmonic mechanical resonator and an input synchronizer. On the main body, symmetrical to the central axle in the plane of the mass centre of the system "main body - operating bodies", accelerators and an equal to their number resonance frequency modulators are located. Each accelerator is connected to a modulator via an operating gear. This gear is meshed with a twice- bigger fifth gear-planet carrier of a resonance frequency modulator. Every second modulator via its fifth left central gear is connected to the first main gear of the phase synchronizer. The other half of the fifth left central gears is connected to the second main gear of the phase synchronizer. One half of all fifth right central gears of any two neighboring modulators are meshed with the large gear ring of the third main gear of the linear amplitude amplifier. The other half of the fifth right central gears is connected to the large gear ring of the fourth main gear of the linear amplitude amplifier. The linear amplitude amplifier is orientated with its small gear rings facing the harmonic mechanical resonator. The small gear ring of the third main gear is meshed with the third gear-planet carrier, and the small gear ring of the fourth main gear is meshed with the fourth gear-planet carrier of an output filter. The output filter is connected to the harmonic mechanical resonator via its third left and right central gears and its fourth left and right central gears. The fourth right central gear of the output filter is directly meshed and the third right central gear through a third parasitic gear is connected to the sixth main gear - second oscillating mass. The fourth left central gear of the output filter is connected through the fourth parasitic gear, and the third left central gear is directly meshed with the fifth main gear - first oscillating mass. The harmonic mechanical resonator is connected to the input synchronizer via the input filters, which are supported by bearings on its first oscillating mass, and the fifth parasitic gears, as well as to the input filters, which are supported by bearings on its second oscillating mass and the sixth parasitic gears. The fifth parasitic gears and the sixth left central gears of the input filters from second oscillating mass are meshed with the seventh main gear of the input synchronizer. The sixth parasitic gears are meshed with the ninth main gear of the input synchronizer. The sixth right central gears of the input filters from the first oscillating mass are meshed with the eighth main gear of the input synchronizer. The seventh main gear of the

input synchronizer via second right central gear and right gear is connected also to the shaft of an engine fixed to the main body. The right gear is mounted at one end of a central shaft, which is supported by bearings in the hollow central axle. The left gear, mounted at the other end of the central shaft, is meshed with first left central gear of the phase synchronizer.

The essence of the invention also involves a phase synchronizer. It is built from first and second main gears, which are freely supported by bearings on the central axle. The first main gear is directly meshed, and the second main gear via the first parasitic gear is connected to the first right central gear of the first elementary epicyclic mechanism, which has two central gears and two satellite gears that are mutually meshed. The planet carrier of the first elementary epicyclic mechanism is shaped like a gear. The first parasitic gear and the first elementary epicyclic mechanism are supported by bearings on the main body. The first left central gear of the first elementary epicyclic mechanism is meshed with the left gear of the central shaft. The first gear-planet carrier is meshed with the first cylindrical worm gear of the first worm mechanism that is used for fixing the dynamic direction of the principal vector of the external lateral forces. The first worm mechanism is fixed to the main body.

The essence of the invention also involves an accelerator. It is built by means of at least two cylindrical holes that are formed in the main body. These cylindrical holes are symmetrically located and their axes are parallel to the central axle. A disk is coaxially fitted in each hole and freely supported by bearings on the main body. A diametrical groove is shaped in each disk, which houses a rotational operating body. Each disk is permanently joined to the main body via the operating body. The mirror position of the grooves of every two disks are fixed; therefore this design uniquely defines the impact direction of the principal vector of the external lateral forces via two permanently meshed identical operating gears. The operating gears are coaxially located and fixed to the face, the first operating gear to the first disk, and the second operating gear to the second disk. One of the operating gears is also meshed with a twice-bigger fifth gear-planet carrier of a resonance frequency modulator.

The essence of the invention also involves a resonance frequency modulator. It is the fifth elementary epicyclic mechanism with two central gears and two mutually meshed satellite gears. The fifth elementary epicyclic mechanism is freely supported by bearings on the main body. The fifth planet carrier is shaped like a gear. The fifth left central gear is meshed with a main gear of the phase synchronizer. The fifth right central gear is meshed with a large gear ring of a main gear from the linear amplitude amplifier. The fifth gear-planet carrier is meshed with an operating gear of an accelerator.

The essence of the invention also involves a linear amplitude amplifier. It is built from two main gears, a gear cluster comprising the third and the fourth gear, each of them with two gear rings - small and large. The gear cluster is freely supported by bearings on the central axle. The third small gear ring is meshed with the third

gear-planet carrier of the output filter. The third and the fourth large gear rings are each meshed with a fifth right central gear of a resonance frequency modulator. The essence of the invention also involves an output filter. It is built from two identical (third and fourth) elementary epicyclic mechanisms with two central gears and mutually meshed two satellite gears. The third and the fourth elementary epicyclic mechanisms are located symmetrically to the central axle. They are freely supported by bearings in the main body. The third gear-planet carrier is mounted from the side of the third left central gear and it is meshed with the third small gear ring of the linear amplitude amplifier. The fourth gear-planet carrier is mounted from the side of the fourth left central gear and it is meshed with the fourth small gear ring of the linear amplitude amplifier. The third parasitic gear is supported by bearings on the main body and it joins third right central gear with fourth right central gear through the sixth main gear - second oscillating mass. The fourth parasitic gear is supported by bearings to the main body and it joins the fourth left central gear with the third left central gear through the fifth main gear - first oscillating mass.

The essence of the invention also involves a harmonic mechanical resonator. It is built from a closed two-mass mechanical oscillating system, rotor-type. The two- mass oscillating system is provided with equal number harmonic vibrators, input filters and parasitic gears, which are located symmetrically to the central axle. A main gear is fixed facially and coaxially to each oscillating first and second masses. The fifth main gear is attached to the first oscillating mass. The sixth main gear is attached to the second oscillating mass. The harmonic vibrators are at least four and they are built from two unbalanced shafts. Each two unbalanced shafts are mutually joined via permanently meshed identical internal and external gears. The mirror positions of the unbalanced masses are fixed and firmly attached, each one to an unbalanced shaft. Each two pairs unbalanced shafts are symmetrically mounted diametrically to the central axle. Each second pair unbalanced shafts are supported by bearings on a different oscillating mass. Each of the internal gears is supported by bearings closer to the central axle and it is meshed second time with personal sixth gear-planet carrier of an input filter, which is mounted on the same oscillating mass.

The essence of the invention also involves an input filter. It is built from the sixth elementary epicyclic mechanism with two central gears and two mutually meshed satellite gears. The sixth elementary epicyclic mechanism is freely supported by bearings on an oscillating mass of the harmonic mechanical resonator. Each sixth gear-planet carrier is mounted from the side of the sixth left central gear and it is meshed with an internal gear of a harmonic vibrator. Each sixth left central gear of an input filter, supported by bearings on the first oscillating mass, is meshed with the fifth parasitic gear. Each sixth right central gear of an input filter, supported by bearings on the second oscillating mass, is meshed with the sixth parasitic gear. The essence of the invention also involves an input synchronizer. It is built from freely supported by bearings on the central axle main seventh, eighth, and ninth

gears. The seventh main gear is directly meshed, and the eighth main gear via the second parasitic gear is connected to the second right central gear of the second elementary epicyclic mechanism, which has two central gears and two mutually meshed satellite gears. The second parasitic gear and the second elementary epicyclic mechanism are supported by bearings on the main body. The second planet carrier is shaped like a gear. The second right central gear is also meshed with the right gear of the central shaft. The second left central gear is meshed with the ninth main gear. The second gear-planet carrier is meshed with the second cylindrical worm gear of the second worm mechanism to control the magnitude of the principal vector of the external lateral forces. The second worm mechanism is fixed to the main body.

The essence of the invention also involves the fact that all force and synchronizing connections of the kinematic chains are executed through gears, chain drives and belt gear drives.

The advantage of the device, in compliance with the invention, is the fact that simple kinematics is ensured for forming, application, fixing, adjustment and control of the parameters of the principal vector of the external lateral force, while accelerated motion is transferred to a material object without changing the system mass and in the absence of high temperatures and pressure, as well as other harmful components accompanying chemical processes.

LIST OF THE ATTACHED FIGURES

Design examples of the invention are shown on the attached figures, as follows: Figure 1 shows the block diagram of the invention Figure 2 - detailed block diagram, according to Fig. 1 Figure 3 - longitudinal mechanical diagram Figure 4 - transverse mechanical diagram, view A from fig. 3 Figure 5 -transverse mechanical diagram, view B from fig. 3 Figure 6 - transverse mechanical diagram, view C from fig. 3 Figure 7 - mechanical diagram of an accelerator, from fig. 6 Figure 8 - dependence chart "time-acceleration" of the system mass centre for a period T using one accelerator

Figure 9 - dependence chart "time-velocity" of the system mass centre for a period T using one accelerator

EXAMPLES FOR INVENTION IMPLEMENTATION

Example for an invention implementation of the device for creation and control of gravitational acceleration, in compliance with the attached Figures 1-7 consists of a main body 1 and attached to its mass centre 16 a hollow central axle 17. On the central axle 17 sequentially and freely supported by bearings in their mass centres are: a phase synchronizer 3, a linear amplitude amplifier 6, a harmonic mechanical resonator 8 and an input synchronizer 10. On the main body 1 , symmetrical to the central axle 17 in the plane 11 of the mass centre 16 of the

system "main body 1 - operating bodies 2", accelerators 4 and an equal to their number resonance frequency modulators 5 are located. Each accelerator 4 is connected to a modulator 5 via an operating gear 34. This gear is meshed with a twice-bigger fifth gear-planet carrier 40 of a resonance frequency modulator 5. Every second modulator 5 via its fifth left central gear 38 is connected to the first main gear 21 of the phase synchronizer 3. The other half of the fifth left central gears 38 is connected to the second main gear 22 of the phase synchronizer 3. One half of all fifth right central gears 39 of any two neighboring modulators 5 are meshed with the large gear ring 45 of the third main gear 41 of the linear amplitude amplifier 6. The other half of the fifth right central gears 39 is connected to the large gear ring 46 of the fourth main gear 42 of the linear amplitude amplifier 6. The linear amplitude amplifier 6 is orientated with its small gear rings 43 and 44 facing the harmonic mechanical resonator 8. The small gear ring 43 of the third main gear 41 is meshed with the third gear - planet carrier 55, and the small gear ring 44 of the fourth main gear 42 is meshed with the fourth gear - planet carrier 56 of an output filter 7. The output filter 7 is connected to the harmonic mechanical resonator 8 via its third left 49 and right 50 central gears and its fourth left 51 and right 52 central gears. The fourth right central gear 52 of the output filter 7 is directly meshed and the third right central gear 50 through a third parasitic gear 53 is connected to the sixth main gear 58 - second oscillating mass 15. The fourth left central gear 51 of the output filter 7 is connected through the fourth parasitic gear 54, and the third left central gear 49 is directly meshed with the fifth main gear 57 - first oscillating mass 14. The harmonic mechanical resonator 8 is connected to the input synchronizer 10 via the input filters 9, which are supported by bearings on its first oscillating mass 14, and the fifth parasitic gears 66, as well as to the input filters 9, which are supported by bearings on its second oscillating mass 15 and the sixth parasitic gears 67. The fifth parasitic gears 66 and the sixth left central gears 63 of the input filters 9 from the second oscillating mass 15 are meshed with the seventh main gear 68 of the input synchronizer 10. The sixth parasitic gears 67 are meshed with the ninth main gear 70 of the input synchronizer 10. The sixth right central gears 64 of the input filters 9 from the first oscillating mass 14 are meshed with the eighth main gear 69 of the input synchronizer 10. The seventh main gear 68 of the input synchronizer 10 via second right central gear 73 and right gear 18 is connected also to the shaft of an engine 78 fixed to the main body 1. The right gear 18 is mounted at one end of a central shaft 19, which is supported by bearings in the hollow central axle 17. The left gear 20, mounted at the other end of the central shaft 19, is meshed with first left central gear 25 of the phase synchronizer 3. The phase synchronizer 3, in compliance with Figure 1 , Figure 2, Figure 3 and Figure 6, is built from first 21 and second 22 main gears, which are freely supported by bearings on the central axle 17. The first main gear 21 is directly meshed, and the second main gear 22 via the first parasitic gear 23 is connected with the first right central gear 26 of the first elementary epicyclic mechanism 24, which has two central gears and two satellite

gears that are mutually meshed. The planet carrier of the first elementary epicyclic mechanism 24 is shaped like a gear 27. The first parasitic gear 23 and the first elementary epicyclic mechanism 24 are supported by bearings on the main body 1. The first left central gear 25 of the first elementary epicyclic mechanism 24 is meshed with the left gear 20 of the central shaft 19. The first gear-planet carrier

27 is meshed with the first cylindrical worm gear 29 of the first worm mechanism

28 that is used for fixing the dynamic direction of the principal vector of the external lateral forces 36. The first worm mechanism 28 is fixed to the main body

1. The accelerator 4, in compliance with Figure 1, Figure 2, Figure 3, Figure 6 and Figure 7, is built by means of at least two cylindrical holes 30 that are formed in the main body 1. These cylindrical holes 30 are symmetrically located and their axes are parallel to the central axle 17. A disk 31 is coaxially fitted in each hole 30 and freely supported by bearings on the main body 1. A diametrical groove 32 is shaped in each disk 31 , which houses a rotational operating body 2. Each disk 31 is permanently joined to the main body 1 via the operating body 2. The mirror position of the grooves 32 of every two disks 31 are fixed; therefore this design uniquely defines the impact direction 35 of the principal vector of the external lateral forces 36 via two permanently meshed identical operating gears 34. The operating gears 34 are coaxially located and fixed to the face, the first operating gear 34 to the first disk 31 , and the second operating gear 34 to the second disk 31. One of the operating gears 34 is also meshed with a twice-bigger fifth gear- planet carrier 40 of a resonance frequency modulator 5. The resonance frequency modulator 5, in compliance with Figure 1 , Figure 2, Figure 3, Figure 6 and Figure 7, is built from fifth elementary epicyclic mechanism 37 with two central gears and two mutually meshed satellite gears. The fifth elementary epicyclic mechanism 37 is freely supported by bearings on the main body 1. The fifth planet carrier is shaped like a gear 40. The fifth left central gear 38 is meshed with main gear 21 , 22 of the phase synchronizer 3. The fifth right central gear 39 is meshed with a large gear ring 45,46 of main gears 41 ,42 from the linear amplitude amplifier 6. The fifth gear-planet carrier 40 is meshed with an operating gear 34 of an accelerator 4. The linear amplitude amplifier 6, in compliance with Figure 1 , Figure

2, Figure 3, and Figure 5, is built from two main gears, a gear cluster comprising the third 41 and the fourth gear 42, each of them with two gear rings - small and large. The gear cluster 41 , 42 is freely supported by bearings on the central axle 17. The third small gear ring 43 is meshed with the third gear-planet carrier 55 of the output filter 7. The fourth small gear ring 44 is meshed with fourth gear-planet carrier 56 of the output 7. The third 45 and the fourth 46 large gear rings are each meshed with a fifth right central gear 39 of a resonance frequency modulator 5. The output filter 7, in compliance with Figure 1 , Figure 2, Figure 4, and Figure 9, is built from two identical (third 47 and fourth 48) elementary epicyclic mechanisms with two central gears and mutually meshed two satellite gears. The third 47 and the fourth 48 elementary epicyclic mechanisms are located symmetrically to the central axle 17. They are freely supported by bearings in the main body 1. The

third gear-planet carrier 55 is, mounted from the side of the .third left centra! gear 49 and it is meshed with the third small gear ring 43 of the linear amplitude amplifier 6. The fourth gear-planet carrier 56 is mounted from the side of the fourth left centfal gear 51 and it is meshed with the fourth small gear ring 44 of the linear amplitude amplifier 6. The third parasitic gear 53 is supported by bearings on the main body 1 and it joins third right central gear 50 with fourth right central gear 52 through the sixth main gear 58 - second oscillating mass 15. The fourth parasitic gear 54 is supported by bearings to the main body 1 and it joins the fourth left central gear 51 with the third left central gear 49 through the fifth main gear 57 - first oscillating mass 14. The harmonic mechanical resonator 8, in compliance with Figure 1 , Figure 2, Figure 3 and Figure 4, is built from a closed two-mass 14 and 15 mechanical oscillating system, rotor-type. The two-mass oscillating system is provided with equal number harmonic vibrators 12, input filters 9 and parasitic gears 66 and 67, which are located symmetrically to the central axle 17. A main gear is fixed facially and coaxially to each oscillating first 14 and second 15 masses. The fifth main gear 57 is attached to the first oscillating mass 14. The sixth main gear 58 is attached to the second oscillating mass 15. The harmonic vibrators 12 are at least four and they are built from two unbalanced shafts 59. Each two unbalanced shafts 59 are mutually joined via permanently meshed identical internal 60 and external 61 gears. The mirror positions of the unbalanced masses 13 are fixed and firmly attached, each one to an unbalanced shaft 59. Each two pairs unbalanced shafts 59 are symmetrically mounted diametrically to the central axle 17. Each second pair unbalanced shafts 59 are supported by bearings on a different oscillating mass 14 and 15. Each of the internal gears 60 is supported by bearings closer to the central axle 17 and it is meshed second time with personal sixth gear-planet carrier 65 of an input filter 9, which is mounted on the same oscillating mass. The input filter 9, in compliance with Figure 1 , Figure 2, Figure 3 and Figure 4, is built from the sixth elementary epicyclic mechanism 62 with two central gears and two mutually meshed satellite gears. The sixth elementary epicyclic mechanism 62 is freely supported by bearings on an oscillating mass 14 or 15 of the harmonic mechanical resonator 8. Each sixth gear-planet carrier 65 is mounted from the side of the sixth left central gear 63 and it is meshed with an internal gear 60 of a harmonic vibrator 12. Each sixth left central gear 63 of an input filter 9, supported by bearings on the first oscillating mass 14, is meshed with the fifth parasitic gear 66. Each sixth right central gear 63 of an input filter 9, supported by bearings on the second oscillating mass 15, is meshed with the sixth parasitic gear 67. The input synchronizer 10, in compliance with Figure 1 , Figure 2, Figure 3 and Figure 4, is built from freely supported by bearings on the central axle 17 main seventh 68, eighth 69, and ninth 70 gears. The seventh main gear 68 is directly meshed, and the eighth main gear 68 via the second parasitic gear 75 is connected to the second right central gear 73 of the second elementary epicyclic mechanism 71 , which has two central gears and two mutually meshed satellite gears. The second parasitic gear 75 and

the second elementary epicyclic mechanism 71 are supported by bearings on the main body 1. The second planet carrier is shaped like a gear 64. The second right central gear 73 is also meshed with the right gear 18 of the central shaft 19. The second left central gear 72 is meshed with the ninth main gear 70. The second gear-planet carrier 74 is meshed with the second cylindrical worm gear 77 of the second worm mechanism 76 to control the magnitude of the principal vector of the external lateral forces 36. The second worm mechanism 76 is fixed to the main body 1.

INVENTION APPLICATION

The device operation, in compliance with the invention, is the following: the engine 78 rotates the central shaft 19, which transfers uniform rotary motion that has a frequency equal to the frequency of the harmonic mechanical resonator 8, to two chains: via its left gear 20 rotates the first left central gear 25 of the first elementary epicyclic mechanism 24 of the phase synchronizer 3, and via its right gear 18 rotates second right central gear 73 of second elementary epicyclic mechanism 71 of the input synchronizer 10. There are two cases: energy distribution only along the left chain and second one after an interaction between the energy flows of the two chains. In both cases the engine 78 start (only for explanation clarity) is considered in case of fixed first 27 and second 74 gears- planet carriers of first 24 and second 71 elementary epicyclic mechanism of the phase 3 and the input 10 synchronizers, which are connected with the worm mechanisms, respectively first 28 to fix and second 76 to control the magnitude of the principal vector of the external lateral forces 36.

Along the left chain, first left central gear 25 is rotated in case of fixed first gear- planet carrier 27. From it via first parasitic gear 23 with the engine direction 78 the first main gear 23 is rotated, and second main gear 22 is directly rotated in the counter direction. Rotated in such a way first 21 and second 22 main gears involve the fifth left central gears 38 of the fifth elementary epicyclic mechanisms 37 of the resonance frequency modulators 5. If there is no signal from the engine 78 at the chain end (fixed fifth right central gears 39 of the modulators 5) all fifth gears-planet carriers 40 reproduce only uniform rotary motion that has a frequency two times less than the resonance frequency, which due to the twice bigger number of their teeth is restored and transferred to the operating gears 34 of the accelerators 4. In this way, both disks 31 of each accelerator 4 create homogeneous rotating mechanical field, and the operating bodies 2 form a force vector in the designed direction 35, which changes under harmonic law, while the vectors of each two accelerators 4, connected via their modulators 5 to second 22 and the other one to first 21 main gear of the phase synchronizer 3 are mutually balanced and force impact on the main body 1 is not achieved. (The magnitude of the principal vector of the external lateral forces 36 is zero.) Along the right chain, seventh main gear 68 via second central gear 73 of second elementary epicyclic mechanism 71 of the input synchronizer 10 is directly rotated

in one direction, and eighth main gear 69 via second parasitic gear 75 and ninth main gear 70 via second right central gear 73 (in case of fixed second planet carrier 74) are rotated in the counter direction. Rotated in such a way: seventh 68, eighth 69 and ninth 70 main gears combined in pairs: seventh main gear 68 via fifth parasitic gear 66, and eighth main gear 69 directly, involve in one and the same direction sixth left 63 and right 64 central gears of the sixth elementary epicyclic mechanisms 62 of the input filters 9, mounted on first oscillating mass 14 and seventh main gear 68 directly, and ninth main gear 70 via sixth parasitic gear 67, rotate in one and the same direction counter to the engine 78 sixth left 63 and right 64 central gears of the sixth elementary epicyclic mechanisms 62 of the input filters 9, mounted on the second oscillating mass 15. Each pair sixth left 63 and right 64 central gears of the input filters 9 neutralizes the motional feedback, which occurs as a result of the angular oscillations of the oscillating masses 14, 15 and drives the sixth planet carriers 65 of the sixth elementary epicyclic mechanisms 62 only with the incoming resonance frequency from the input synchronizer 10. In this way, the sixth gears-planet carriers 65 from the first oscillating mass 14 are uniformly rotated in the same direction as the engine 78, and the sixth gears-planet carriers 65 from the second oscillating mass 15 are uniformly rotated but in the counter direction, while via meshed with them internal gears 60 in the same way are also rotated the unbalanced shafts 59 of the harmonic vibrators 12. The unbalanced shafts 59 of each pair unbalanced vibrators are rotated synchronously and antiphasely via permanently meshed identical internal 60 and external 61 gears, while the mirror position fixed unbalanced masses 13 during their movement without changing the inertial characteristics of both oscillating masses 14, 15, and thence ensuring constant natural frequency of the harmonic mechanical resonator 8, create exciting forces of centrifugal nature, the radial components of which always balance each other, and the tangential components are added. Symmetrically and diametrically arranged harmonic vibrators 12 exert two antiphase couples of forces on the harmonic mechanical resonator 8, which change under harmonic law with frequency equal to its natural frequency, force the oscillating masses 14 and 15 to make resonance angular oscillation and form the dynamic parameters of the harmonic vibratory field. These parameters are transferred through the output filter 7 and the linear amplitude amplifier 6 to the resonance frequency modulators 5, while the sixth main gear-planet carrier 58 - second oscillating mass 15 transfers oscillation (rotates with variable angular velocity) with the direction of the engine 78 to third right central gear 50 via sixth parasitic gear 54 and directly in the counter direction to the fourth right central gear 52 from third 47 and fourth 48 elementary epicyclic mechanisms of the output filter 7, and the fifth main gear 57 - first oscillating mass 14 transfers oscillation in the counter direction to fourth left central gear 51 via fifth parasitic gear 53 and directly to third left central gear 49. In this way, the output filter 7 excluding a feedback influence, eventually originated by the second degree of freedom (the second main form of movement)

of the harmonic mechanical resonator 8, reproduces on its planet carriers (third 55 and fourth 56) the averaged dynamic parameters of the vibratory field. The third gear-planet carrier 55 transfers oscillation in phase with the direction of the engine 78 via the small gear ring 43 to third main gear 41 of the linear amplitude amplifier 6, and the fourth gear-planet carrier 56 transfers oscillation in antiphase via the small gear ring 44 to the fourth main gear 42. Both main third 41 and fourth 42 gears drive all fifth right central gears 39 of the fifth elementary epicyclic mechanisms 37 of the resonance frequency modulators 5, half of them in antiphase variable harmonic motions (deliver to them modulation signals, which change synchronously in antiphase under harmonic law) with frequency and amplitude values of the vibratory velocity equal in magnitude to the angular velocity of the engine 78. In this way, both chains, left and right, along which is supplied and converted the energy of the engine 78, interact once again in every resonance frequency modulator 5. During the time intervals, at which the movements of each two fifth left 38 and right 39 central gears are in phase, the rotation of the fifth gear-planet carrier 40 is accelerated, while they are in antiphase it is decelerated. At such supplied energy flows, ensured by stable qualitative and quantitative characteristics within each time interval, the fifth gears-planet carriers 40 accomplish variable rotary motion, reaching half of the angular velocity of the engine 78 during their acceleration, while decelerating after one half of the period T (π/2 rad) it becomes zero, as motions of all fifth gears- planet carriers 40 are synchronous - half of them in phase, and the other half in antiphase. Motions with such a nature of the parameters but with maximum equal to the angular velocity of the engine 78 are also transferred to the operating gears 34 of the accelerators 4 via each twice-bigger fifth gear-planet carrier 40, while both disks 31 of each accelerator 4 accomplish synchronous inhorηogeneous rotating mechanical field and each two accelerators 4, connected through their modulators 5 to second main gear 22, and the other one to first main gear 21 of the phase synchronizer 3, have antiphase and dephased at π rad fields. The disks 31 of each accelerator 4 through the walls of their grooves 32 force the operating bodies 2 to make rotating uniformly-variable motions with periodically variable tangential velocity from a minimum (zero) to a maximum value and vice versa with extreme values, dephased at π rad (the phase angle of the rotating uniformly- variable accelerated motion is equal to the integrated variable frequency for one period) restricting the dynamic direction of the impact. Periodically variable kinetic energy of the disks 31 creates periodically variable unbalanced forces of centrifugal nature in the operating bodies 2. The operating bodies 2 act upon the walls of the cylindrical holes of the main body 1. The transverse force components are mutually neutralized, and the longitudinal force components along the designed impact direction 35 are added. The sum of all variable unbalanced forces along the impact direction 35 from all accelerators 4 forms the principal vector of the external lateral forces 36, which is applied on the main body 1 to the mass centre 16 of the system "main body 1 - operating bodies 2". In this way, the

principal vector of the external lateral forces 36 changes along the impact direction 35 the momentum of the system "main body 1 - operating bodies 2" and transfers to it normal acceleration.

In general, the maximum of the modulated motion is dephased according to the designed direction 35 for force impact (the dynamic direction and the designed direction 35 do not coincide). Therefore, a single nullifying of that phase is necessary after each start of the engine 78. For that purpose, the first gear-planet carrier 27 of the first elementary epicyclic mechanism 24 of the phase synchronizer 3 is rotated via first cylindrical worm gear 29 of the first worm mechanism 28 for fixing the direction of the principal vector of the external lateral forces 36, while using directly first left central gear 25 and via first parasitic gear 23 is accomplished a synchronous delay of the antiphase uniform rotary motions of first 21 and second 22 main gears, and through them to all fifth left central gears 38 of the fifth elementary epicyclic mechanisms 37 of the resonance frequency modulators 5 until the total coincidence of the maximum of the modulated motion with the moment, when all grooves 32 of the disks 31 of the accelerators 4 become parallel.

The magnitude control of the principal vector of the external lateral forces 36 is achieved by altering the modulation depth, which is proportional to the resonance amplitude of the harmonic mechanical resonator 8. The second gear-planet carrier 74 of the second elementary epicyclic mechanism 71 of the input synchronizer 10 is rotated via the second cylindrical worm gear 77 of the second worm mechanism 76 for magnitude control of the principal vector of the external lateral forces 36, which is permanently meshed with it. The second planet carrier 74 rotates via two mutually meshed satellite gears with one and the same velocity and direction both second left 72 and right 73 central gears. Seventh 68 and ninth 70 main gears, which are permanently meshed with them, also are rotated in the same direction, and the eighth main gear 69 is rotated in antiphase via the second parasitic gear 75. Rotated in antiphase, seventh 68 and eighth 69 main gear, the former one 68 via fifth parasitic gear 66, and the later one 69 directly, rotate in phase the sixth left 63 and right 64 central gears of the input filters 9 of first oscillating mass 14, which via two blocked and mutually meshed satellite gears of the sixth elementary epicyclic mechanisms 62 rotate their planet carriers 65, and they rotate the unbalanced shafts 59 of the harmonic vibrators 12, while the input filters 9 from the second oscillating mass 15 via two mutually meshed satellite gears of the sixth epicyclic mechanisms 62, which rotate synchronously one toward the other with one and the same velocity via rotating in antiphase both sixth left 63 and right 64 central gears, the former one 63 directly and the later one 64 via sixth parasitic gear 67, driven by the rotating in phase seventh 68 and ninth 70 main gears, do not transfer motion to the sixth gears-planet carriers 65 and the unbalanced shafts 59 of the harmonic vibrators 12, connected to them via the internal 60 and external 61 gears, remain static. In this way is achieved stepless dephasing of the unbalanced masses 13 from the harmonic vibrators 12, which

excite first oscillating mass 14, with regard to the unbalanced masses 13 from the harmonic vibrators 12, which excite second oscillating mass 15. In case of dephasing at rad, which is used for mirror position fixing of the unbalanced masses 13 from the harmonic vibrators 12 - one of the oscillating masses is fixed externally, and to the other one internally, the resonance amplitude of the oscillations of the harmonic mechanical resonator decreases to zero and modulation is not accomplished. Contrariwise, when mirror position fixing of all unbalanced masses 13 of all harmonic vibrators 12 is achieved only internally or externally, the resonance amplitude of the oscillations is maximum, respectively maximum are the modulation depth and the magnitude of the principal vector of the external lateral forces 36 and maximum acceleration is achieved. The result of the method implementation from a dynamic point of view is illustrated on Figure 8. The chart "time-acceleration" of the system mass centre illustrates the fact that for every period T the mean integral value is different from zero. The result of the method implementation from a kinematic point of view is illustrated on Figure 9. The chart "time-velocity" of the system mass centre illustrates the fact that the mean integral value is different from zero. The magnitude of the ordinate - V at the end of the period T shows the velocity increment of the system mass centre in the controlled direction for every period T. In compliance with the invention, this increment is four times bigger.

REFERENCE

[1] Toshev S. D., Baev IA ₁ Marinov M. G., Bonchev LP., Physics, Sofia, Nauka i

Izkustvo, 1987

[2] Pisarev A.M., Paraskov Tz. N., Bachvarov S. N., A Course in Theoretical

Mechanics. Part II, Sofia, Technika, 1988

[3] Einstein A., Physics and Reality, Moscow, Nauka, 1965

[4] Gulia N.V., Inertia, Moscow, Nauka, 1982

[5] Patent No BG 52155