WO2007124515A1

WO2007124515A1 - Counter-rotation drive

Info

Publication number: WO2007124515A1
Application number: PCT/YU2006/000008
Authority: WO
Inventors: Marko Ivankovic
Original assignee: Individual
Current assignee: Individual
Priority date: 2006-04-26
Filing date: 2006-04-26
Publication date: 2007-11-01
Anticipated expiration: 2008-10-26

Abstract

The mechanical counter-rotation drive is based on the laws of relative motion of an eccentric part of one of at least two shafts with respect to the plates of a determined shape whose motion is confined by pins arranged in a determined arrangement, where in the housing (10) are accommodated the first (driving) plate (30) and the second (driven) plate (40) in such a manner that they are parallel to one another. In the housing (10) are embedded a plurality of pins (20) of which each one represents a shaft which bears and around which rotates at least one cylinder (35) which is in operational contact with the perimeter (135) of the first plate (30) which is in rigid contact with the first shaft (50). In the first plate (30) are embedded a plurality of second pins (80) of which each one represents a shaft which bears and around which rotates at least one cylinder (85) which is in operational contact with the perimeter (145) of the second plate (40). The angular direction of rotation of the first shaft (50) is the first direction (55), while the angular direction of rotation of the second (60) shaft is (65), such that the angular directions of rotation (55 and 65) are opposite to each other.

Description

COUNTER-ROTATION DRIVE

Field of the invention

The present invention belongs to the field of mechanical engineering, namely to mechanical elements or assemblies, and relates to transmission systems, and more particularly to transmission systems with rotating plates capable of producing counter-rotation between two coupled shafts. Counter-rotation is used in mechanisms which require reversing the angular direction of rotation, in cases in which it is necessary for the driving shaft to rotate in one angular direction, and the other shaft, which is driven by the driving shaft, to rotate in the opposite angular direction. Such forms of transmission are used in helicopter drives, differential transmissions in vehicles, propeller driven marine vessels, turbine engines, turbogenerators, compressors, etc.

According International Patent Classification (IPC) invention belongs to class F16D.

Technical problem

Technical problem is realization of solution for counter-rotation suitable for use in the field of all drive mechanisms with propellers, turbines, compressors with blades, in all drive transmissions in which reversing the angular direction of rotation is required, e.g. in differential transmissions in cars and other land vehicles, submarine drive systems, torpedoes, in precision mechanical mechanisms generally and robotics particularly, especially in designing combustion gas turbine engines in which a substantial enhancement of efficiency can be achieved by counter-rotation of parts of the compressor and other parts of the engine, with better use of the input energy per compression stage. Enhancement of efficiency reduces the consumption of fuel per unit of distance covered, which reduces environmental pollution. In addition, improved efficiency offers improvements in the economy of engine design, as well as of the whole vehicle, vessel, or flying equipment.

The present invention solves the problem of realization of mechanical counter-rotation without planetary transmission elements, which provides counter-rotation of driven shaft with a transmission ratio of 1 :1, whereas in numerous embodiments of the invention it is possible to realize transmission ratios other than 1:1, whereby the driving shaft and driven shaft share a common rotational axis, and transmission will be realized by use of rotating, mutually separately operationally connected plates within the same housing. There is also need for solving the problem of realization of counter-rotation drive wherein the part of the assembly which is functionally the driving part in one embodiment can in another embodiment be functionally the driven part and vice versa.

State of the Art

Prior art comprise known solutions of solving the problem of mechanical counter- rotation with a transmission ratio of 1 to 1 and shafts aligned along a common rotational axis, but these solutions have been realized only exclusively by use of planetary gear transmissions, which are based upon gears and transmission of torque via gears. Such is, for example, a solution with a double propeller helicopter with a common axis by S. P. Vaughn (US Patent 2,037,745 of April 21, 1936) where counter-rotation of two propeller systems is used to provide a more stable flight and facilitate the control of the helicopter. A solution with a counter-rotating double propeller system US Patent 4,642,059 A of Feb.10, 1987 (Nohara) is used for a marine drive, in which case an inner shaft is at one end directly coupled to an outer hollow drive shaft. Another patent US 4,963,108 A Oct.16, 1990 (Koda et al.) describes a system for counter-rotation comprising a propeller with a large gear driven by an engine, with which gear a plurality of smaller gears are in operational contact at its perimeter, so that counter-rotation of the second, driven, shaft is obtained. The known solutions which use planetary geared transmission are always cumbersome, with significant losses to friction, accompanied by common problems of low efficiency, due to gaps which cannot be avoided in such solutions. These solutions are also known to produce clattering and loud noise which results from the existence of the gaps. Such transmission systems also have a low degree of safety of operation, and are known to lack a constant torque in each point. Also, in solutions with planetary gears, the load is unevenly distributed, in most cases concentrated into one point (the point of immediate contact of the driving and driven part of the assembly) which creates critical elements in the assembly and requires unrealistically large mechanism needed to provide necessary safety of operation.

The problem of obtaining counter-rotation of coupled shafts with a transmission ratio of 1:1 and shafts aligned along the same rotational axis in the manner disclosed here has not been observed in any other solution known in prior art either. Description of the invention

The present invention relates to a mechanical counter-rotation drive, which provides mechanical counter-rotation of shafts coupled by the invention with a transmission ratio of 1:1 and aligned along a common rotational axis without planetary transmission elements, whereas in numerous embodiments of the invention it is possible to realize transmission ratios other than 1:1. The basic embodiment of the invention is the realization of a mechanism for reversing the angular direction of rotation between two shafts which rotate with angular directions of rotation that are opposite to each other, and said shafts share a common rotational axis. The present invention can generally be used for precise reversing of the angular direction of rotation with a common axis, and particularly in combustion gas turbine engines, turbine engines in general, torque transmissions to propellers, helicopter drives, marine drives, differential transmissions, land vehicles, robotics, etc.

Brief Description of the Drawings

The above-mentioned and other concepts of the present invention will now be described with reference to the accompanying drawings of the exemplary and preferred embodiment of the present invention. The presented embodiment is intended to illustrate the application, but not to limit the invention. The drawings contain the following figures, in which like numbers refer to like parts throughout the description and drawings and wherein:

Figure 1 is a perspective view of the counter-rotation drive according to the invention in which part of the housing has been removed;

Figure 2 is a cross-sectional view of the counter-rotation drive along the R-R section as marked in Figure 1 ;

Figure 3 is an illustration of a typical first (driving) plate as applied in the preferred embodiment illustrated in Figure 1 ;

Figure 4 is an illustration of a typical second (driven) plate as applied in the preferred embodiment illustrated in Figure 1 ;

Figure 5 is a representation of the core assembly of the first plate and the second plate with their typical accessories as applied in the preferred embodiment illustrated in Figure 1. Detailed Description of the Invention

A counter-rotation drive according to the present invention is illustrated in Figure 1, in which the housing 10 which supports the whole counter-rotation drive accommodates the first (driving) plate 30 and the second (driven) plate 40 in such a manner that they are approximately or completely parallel to one another. In the housing 10 are embedded a plurality of pins 20 of which each one represents an axis which bears and around which rotates at least one cylinder 35 which is in operational contact with the perimeter 135 of the first plate 30 which is in rigid contact with the first shaft 50 (which shaft is not visible in Figure 1). In the first plate 30 are embedded a plurality of second pins 80 of which each one represents an axis which bears and around which rotates at least one cylinder 85 which is in operational contact with the perimeter 145 of the second plate 40. Ball bearings 90 act as a sliding support for the second shaft 60 in the part 10a of the housing, which part is in this case removed in order to allow the view of the design of the counter-rotation drive according to the invention inside the housing 10. In the preferred embodiment the sliding support of the first shaft 50 in the housing 10 and/or the second shaft 60 in the part of the housing 10a is realized by ball bearings, but the sliding support can be realized by using other sliding elements and/or sliding surfaces. The axis of rotation of the first shaft 50, which is not visible in Figure 1, belongs approximately or exactly to the same line as the axis of rotation of the second shaft 60, and the angular direction of rotation of the first shaft 50 is the first direction 55, while the angular direction of rotation of the second 60 shaft is 65, such that the angular directions of rotation 55 and 65 are opposite to each other.

Referring to Figure 2 which illustrates the R-R cross-section marked in Figure 1, but in a complete and closed housing 10, in which both parts of the housing 10 and.10a are joined together at the interface 100, the counter-rotation drive according to the invention comprises the first shaft 50 which rotates in the first angular direction 55 around the axis of rotation 56 which approximately or exactly lies on the same line as the axis of rotation 66 of the second shaft 60 which rotates in the second angular direction of rotation 65. The first shaft 50 comprises an eccentric part 70 or is in rigid contact with it, such that the axis 75 of the eccentric part is eccentrically offset with respect to the axis of rotation 56 of the first shaft 50. The eccentric part 70 is supported in the first plate 30 via ball bearings 95, instead of which bearings other rolling or sliding elements and/or surfaces can be used. Referring to Figures 1 and 2, the first (driving) shaft 50 which rotates in the first angular direction 55 comprises an eccentric part 70 which is operationally connected to the first plate 30. The first plate 30 moves within a space confined by a set of pins 20 in such a way that the surface of the perimeter 135 of the first plate 30 with lobes 130 and recesses between them will move over the surfaces of rotating cylinders 35 on pins 20, so that the rotation of the driving shaft 50 in the first angular direction 55, due to the eccentric part 70, will produce a revolution of axis 75 around axis 56, whereby the center of plate 30 will also move around the axis 56, and the sliding of the lobes 130, or recesses between the lobes, over the surfaces of the rotating cylinders 35 on pins 20 will produce rotational motion of the first plate 30 in the second angular direction 65. The first angular direction of rotation 55 and the second angular direction of rotation 65 are opposite to one another. For example, if the first angular direction of rotation 55 is a clockwise direction, the other angular direction of rotation 65 is a counterclockwise direction. The first plate 30 is operationally coupled with the second plate 40 (via the second pins 80) and causes the second plate 40 to move also in the second angular direction of rotation 65. The driven shaft 60 is rigidly connected to the second plate 40 and provides the output torque. The first pins 20 can be placed within the housing 10 or within another operational space of another assembly that is adapted and stationary with respect to the housing 10. The axes 21 of the first pins 20 are approximately perpendicular to the first plate 30 and the second plate 40.

Figure 3 is a representation of the first (driving) plate 30. It is represented here as a plate with three lobes 130 (or, alternatively three recesses between them), which are at a distance from the center 136 of the plate 30, but the first plate can have more lobes and/or recesses. The first plate 30 has such a shape that the surface of the perimeter 135 of the first plate 30 is in contact with pins 20 via their rotating cylinders 35 supported in the housing 10, 10a (see Figure 2), although generally it is not required for the first plate to be in constant contact with all pins and/or cylinders of the rolling/sliding elements. The motion of the first plate 30 is achieved by rotation of shaft 50 with the eccentric part 70, supported in the housing 10 and in the center or approximate center 136 of the first plate 30. The first plate 30 is operationally connected with the first driving shaft 50 via its eccentric part 70 which has an axis 75 (see Figure 2). The eccentric part 70 is supported in the centre or approximate centre 136 of the first plate 30. It is not required for the eccentric part 70 of the first shaft 50 to be operationally connected with the first plate 30 approximately in the centre of the first plate 30, but it is preferred. The eccentric part 70 with axis 75 (see Figure 2) is designed and configured so that it fits the driving plate 30. The size and thickness of the first plate 30 depends on the application. However, the size and thickness of the first plate 30 may vary depending on the magnitude of the drive torque. For example, if a large torque is applied, it may require a large first plate in order for it to withstand structural and dynamical stress caused by the torque.

Figure 4 is an illustration of a typical second plate 40 with two lobes 140 at a distance from the center 146 of the second plate 40. Generally the second plate 40 can have more lobes. The second plate 40 has a perimeter 145 such that during motion a portion of the surface of the perimeter remains in contact with the rotating cylinders 85 of the second pins 80 of the first plate 30, although it is not a general requirement that the second plate be in constant contact with all the pins and/or cylinders of the rolling/sliding elements (see Figure 1 and Figure 2). The shape of the perimeter 145 of the second plate 40 is not arbitrary, but determined by trigonometric function which causes the lobes 140 of the second plate 40 to be in contact with the rotating cylinders 85 of the second pins 80 of the first plate 30 (see Figure 1 and Figure 2).

The first plate 30 and the second plate 40 can be constructed and produced by any suitable method known to a person skilled in the art, from any suitable material such as metal, wood, plastic, composites, alloys, or ceramics, or any existing material in solid form. Selection of the first plate 30 and second plate 40 material should be commensurate with the particular application. However, it is not required that the material selection for first drive 30 and second drive 40 be commensurate with the particular application, but may be selected based on economic considerations such as cheapest to produce. Furthermore, the first plate 30 and the second plate 40 are not required to be constructed of the same material. Both plates can have additional holes, lobes, incisions, notches and any other elements of shape. It is also anticipated, in another embodiment, to double the first plate 30 and its eccentric part 70 in such a way that these two first plates have the opposite distribution of mass and thereby cancel out vibrations that are the result of the uneven distribution of mass of a single first plate.

In Figure 5 the first plate 30 is illustrated as a plate with three lobes, and the second plate 40 with two lobes. The first pins 20 which are supported in the housing 10 (see Figure 2) are, via the rotating cylinders 35, in a rolling/sliding contact with the surface of the perimeter 135 of the first plate 30. The second pins 80, which are in this case supported in the first plate 30, are via the rotating cylinders 85 in a rolling/sliding contact with the surface of the perimeter 145 of the first plate 40. It is preferred that each of the second pins 80 be placed in the domains of the lobes 130 of the first plate 30 (see Figure 3) although they can be placed in the domain of the recesses if required. Each of the second pins 80 is placed at a determined distance from the center of the first plate 30. The number of lobes 130 of the first plate 30 is not arbitrary. That number will affect the reduction or increase of the speed of rotation of the second shaft 60. The positions of the second pins 80 are a function of the shape of the perimeter 145.

The housing 10 (Figure 2) comprises two parts (10 and 10a) which are connected to each other at interface 100, but, depending on construction requirements related to preferred application, housing 10 may be constructed from as much parts as needed. Each first pin 20 further comprises rotating cylinder 35 placed in such a way that it can rotate around part of the pin 20. It is illustrated that each rotating cylinder 35 is supported between part of the housing 10 and part of the housing 10a, thereby its translatory motion being limited. Instead of application only rotating cylinder 35, ball bearings can be used or cylinders may be on ball bearings, which are on pin or pins 20 and may be, via ball bearings, supported in housing 10 or may be supported in or operationally connected with working space of some another assembly inside which counter-rotation drive assembly is mounted. Each rotating cylinder 35 freely rotates around corresponding first pin 20. Each cylinder 35 is made of any suitable material. Each rotating cylinder 85 freely rotates around corresponding second pin 80. Each cylinder 85 is made of any suitable material. This way of pin and rotating cylinder construction is not required generally, as rotating cylinders 35 and 85, i.e., rolling or sliding elements, may be operationally assembled in any suitable way into housing 10, i.e., onto plate 30. The first (driving) shaft 50 is supported via the bearings 90 in the housing 10, or within some other assembly, and has an axis of rotation 56. If required, more than one set of bearings 90 can be used for the support of the shaft 50. The first plate 30 comprises a plurality of second pins 80 whose axes 81 are approximately or exactly parallel to axes 21 of the first pins 20, although this is not a general requirement, but the outer surfaces of the rotating cylinders 35 and 85 must be approximately or exactly parallel to the surfaces of the perimeters 135 and 145, which represent the contact surface of the plates 30 and 40. It is advantageous that the first pins 20 and the second pins 80 be fixed by screws 25. However, this is not a general requirement, but the most simple solution, while other solutions are also applicable. The second (driven) shaft 60, whose axis of rotation is axis 66, is operationally coupled to the second plate 40. However, this is not a general requirement, since the second shaft 60 and the second plate 40 can be made e.g. out of a single piece of material. The second shaft 60 is supported in the bearings 90 mounted within the housing 10 or within some other assembly. The axis of rotation 56 of the driving shaft 50 and the axis of rotation 66 of the driven shaft 60 belong approximately or exactly to the same line and remain so during operation.

The speed and motion of the first plate 30 depends on the shape of its perimeter 135, number of lobes 130, number of pins 20 supported in the housing 10, and is determined by the trigonometric function which causes the pins 20 to impinge on the lobes 130 of the first plate 30, thereby rotating it in the desired direction around its center 136 with the axis of rotation 75. The rotation of the second plate 40 is produced by the transmission of the rotation of the first plate 30 via the second pins 80 to the second plate 40. The angular speed of rotation of the second plate 40 can be different from the angular speed of rotation of the first plate 30. The angular speed and motion of the second plate 40 is determined by the number of lobes 130 of the first plate 30, the number of lobes 140 of the second plate 40, the shape of the perimeter 135 of the first plate 30 and the of the perimeter 145 of the second plate 40. It is not required that each lobe 130 comprises a second pin 80 placed in the domain of the lobe. The constellation described produces rotation of the first plate in the opposite angular direction of rotation 65 from the angular direction of rotation 55 of the first shaft 50. Thus, correct placement of the first pins 80 and the shape of the perimeter 135 of the first plate 30, particularly of lobes 130, are essential for obtaining counter-rotation. In addition, the magnitude of the distance of the center of the first plate 30 from the center of rotation 56 of the first shaft 50, i.e. the magnitude of the eccentric offset 70, is the variable that affects the trigonometric function which defines the shape of the perimeter 135 of the first plate 30.

It is important to note that the driving plate can be either plate 30 or plate 40, but the present description only deals with the case in which the drive plate is plate 30, for simplicity. In the same way, the driving shaft can be either shaft 50 or shaft 60. In other words, the part of the assembly which is functionally the driving part in one embodiment can in another embodiment be functionally the driven part and vice versa. This is applies to all descriptions and examples in further text.

In yet another embodiment, the same principles provide a solution which effectively comprises two basic embodiments described above joined into one, in such a way that it includes two first plates 30 and two eccentric parts 70, and the second plates 40 are rigidly joined into one part, and the counter-rotation is from that part transferred by a rigid connection outside the housing to a disk which rotates in the opposite angular direction with respect to the first shaft 50, which shaft in such a design passes through the whole assembly. This design provides perfect operational balance of the assembly.

In yet another embodiment the same principles provide a solution which effectively comprises two basic embodiments described above joined into one, in such a way that the second shaft 60 has a larger diameter than the first shaft 50 and by requirement is hollow, so that the first shaft 50 passes through it and shares the axis of rotation with the second shaft 60, which causes the counter-rotation of the second shaft 60 around the first shaft 50 which in such a design passes through the whole assembly.

In yet another embodiment, combining and pairing of the plates (driving and driven, i.e. the first and the second plates) it is also possible to achieve various transmission ratios. For example, if the first plate is made with e.g. 6 lobes and the second plate with 4 lobes, with the same conditions as in the above described embodiments, a transmission ratio different from 1 : 1 is achieved. Also, if the same plates are used as for achieving the transmission ratio of 1:1, but with different conditions such as the number of first pins 20 in the housing 10 and the size of the eccentric shift of the eccentric part 70 of the first shaft 50, yet another transmission ratio different from 1 : 1 is achieved. By adding one more first plate by pairing in such a way that a sequence first-second-first plate is obtained, the transmission ratio of 1:1 is maintained, but the first and the last shaft in the sequence rotate in the same angular direction of rotation.

In yet another embodiment, the present invention is used in designing and constructing the compressor of a combustion gas turbine engine such that the compressor comprises a plurality of propellers and/or disks with blades, of which the first propeller, or a plurality of the first propellers, rotate in the first angular direction of rotation and the second propeller, or a plurality of the second propellers, rotate in the second angular direction of rotation. In this embodiment, the first propellers are operationally connected to the first shaft 50, and the second propellers are operationally connected to the second shaft 60. These propellers can be arranged in any required or advantageous arrangement. Also, if it is necessary or required, said compressor can comprise stationary propellers as well. Therefore, counter-rotation drive according to the present invention may be used for reduction of the stage count in the compressor section of a typical combustion turbine engine.

In other embodiments, the counter-rotation drive can be applied in any design with drive shafts, such as the marine propeller drives, helicopter propeller drives, cars, and home appliances, to name a few. La such applications the counter-rotation drive according to the invention would provide counter-rotation and cancellation of the torque.

Furthermore, other embodiments of the counter-rotation drive according to the invention are possible in turbo-propulsion engines, turbo-shaft engines, turbo-fan engines, other turbine engines, in differential transmissions in cars and other land vehicles, submarine drive systems or that of torpedoes, in robotics for precise transmission of motion, etc.

Furthermore, while the counter-rotation drive is disclosed here in the context of application as a drive system, it is not limited to applications as a drive system. The counter- rotation drive according to the invention can also be used as a reduction system. A person skilled in the art can find other applications, processes, configurations, and methods for the counter-rotation drive hereby disclosed. Because of that, the illustration and description of the present invention in the context of application as a counter-rotating drive is only one of possible applications of the present invention.

Examples

Further in the text examples are given which should serve solely for illustration of possible embodiments of the present invention, without limiting the scope of the invention in any way.

Examples 1

The basic embodiment of the counter-rotation drive

An embodiment of the counter-rotation drive is illustrated in Figures 1 to 5 in which the rotation in the first angular direction 55 of the first (driving) shaft 50 with its eccentric part 70 drives the first (driving) plate 30 that exercises translational motion while rotating between pins 20 which are placed within the housing 10 of the counter-rotation drive and which force the first plate 30 to move along a determined path, the same path along which move the second pins 80 that are placed on the first plate 30, and which thereby drive the second (driven) plate 40, since it also has the shape of the same path. Counter-rotation is achieved as a result of the motion of the eccentric part 70 which forces the first plate 30 to rotate in the opposite angular direction from the angular direction of the first shaft 50, because it is the only possible direction, due to the arrangement of the pins 20 in the housing 10 and the shape 135 of the first plate 30.

A physical model was made according to this embodiment, which model is easily driven manually, and allowed measurement of the transmission, which was 1 : 1 in this case. The model dimensions are: diameter 350 mm, both shafts diameter 25 mm, eccentric offset of the eccentric part of the shaft 11.25 mm.

Example 2

Embodiment of counter-rotation drive capable of high rotational speeds According to the embodiment of the present invention with a transmission ratio of 1 : 1 a physical model was made of metal, with similar basic dimensions as in Example 1. This metal model was used to test the possibility of achieving high rotational speeds. The rotational speeds applied to the model were in excess of 100 000 RPM (one hundred thousand revolutions per minute). The test confirmed that the overall friction in this embodiment originates almost exclusively from the friction present in the bearings while rolling, and the heat generated is exclusively associated with the bearings and their motion. By using good quality bearings and special lubricants and lubrication systems, this energy loss is minimized and rendered practically negligible.

This model was also tested for mechanical breakdown, and showed to be completely resistant to all stresses anticipated by design. It was confirmed that a plurality of physical damages would be required to happen simultaneously to induce a breakdown and render the whole device disfunctional. This showed that the safety factor of a counter-rotation drive is much higher than that of classical gear transmission devices.

While the counter-rotation drive according to the invention has been described in connection with preferred and particular embodiments, the invention is not limited only to illustrated and described realizations, it is to be understood that its modifications, equivalents, and variations will be obvious, without changing the essence of the invention, to persons skilled in the art upon reading the description disclosed herein, and therefore it is the intention of the author for these possible embodiments to be included within the spirit and scope of the appended patent claims.

Claims

1. A mechanical counter-rotation drive, which is used for reversing the angular direction of rotation of the drive torque with purpose of its transmission in compressors of combustion gas turbine engines, turbines of combustion gas turbine engines and other turbine engines, in differential transmissions, helicopter propeller drives, marine vessel propeller drives, other drives of fans and propellers, other transmission systems with reversing of angular direction of the rotation and similar, wherein in the housing (10, 10a), with interface which supports the counter-rotation drive, the first plate (30) and the second plate (40) are accommodated in such a manner that they are approximately or completely parallel to one another, where in the housing (10, 10a) a plurality of pins (20) are slidingly embedded with axis (21) which is approximately perpendicular to surfaces of plates (30, 40), where these pins (20) bear and around them rotates at least one cylinder (35) which is in a rolling or sliding contact with part of the surface of the perimeter (135) of the first plate (30), where the first plate (30) is in rigid contact with the first shaft (50), supported in the housing (10) via bearings (90), and where shaft (50) has eccentric part (70) at its end, wherein eccentric part (70) is supported in the first plate (3Q) via bearings (95), where in the first plate (30) are embedded a plurality of second pins (80) with axis (81), where each pin (80) represents an axis which bears and around which rotates at least one cylinder (85) which is in operational contact with part of the perimeter (145) surface of the second plate (40), and where ball bearings (90) act as a sliding support for the second shaft (60) in the part (10a) of the housing, and where the sliding support of the first shaft (50) in the housing (10) and/or the second shaft (60) in the housing (10a) is realized by ball bearings, or by using other sliding elements, i.e., sliding surfaces, where the axis (56) of rotation of the first shaft (50) with angular direction of rotation (55) is approximately or exactly on the same line as the axis (66) of rotation of the second shaft (60) with angular direction of the rotation (65), where directions (55) and (65) are opposite to each other.

2. The mechanical counter-rotation drive according to claim 1, wherein the first plate (30) has three or more lobes (130) with recesses between them, and center (136) with bearing (95) within which eccentric part (70) is supported, where center (136) is not in the same line with axis (56) of rotation of the first shaft (50) nor with axis (66) of rotation of the second shaft (60).

3. The mechanical counter-rotation drive according to claims 1 and 2, wherein the first plate (30) is located within a space confined by a set of pins (20) in such a way that the surface of the perimeter (135) of the first plate (30) with lobes (130) and recesses between them will move over the surfaces of rotating cylinders (35) on pins (20), so that the rotation of the driving shaft (50) in the first angular direction (55), due to the eccentric part (70), will produce a revolution of axis (75) around axis (56), whereby the center (136) of plate (30) will also move around the axis (56), and the sliding of the lobes (130), and recesses between the lobes, over the surfaces of the rotating cylinders (35) on pins (20) will produce rotational motion of the first plate (30) in the second angular direction (65), where the first angular direction of rotation (55) and the second angular direction of rotation (65) are opposite to one another.

4. The mechanical counter-rotation drive according to claims 1-3, wherein second plate (40) has two or more lobes (140) with recesses between them, at equal distances from the center (146) of the second plate (40) in which center the second shaft (60) is rigidly connected.

5. The mechanical counter-rotation drive according to claims 1-4, wherein the number of the lobes (130) on the first plate (30) is operationally connected with a number of lobes (140) on the second plate (40), number and arrangement of the first pins (20) and number and arrangement of the second pins (80).

6. The mechanical counter-rotation drive according to claims 1-5, wherein the second pins (80) are placed in the domains of the lobes (130) of the first plate (30) and all pins (80) are at equal angular distance on the plate (30), where this angular distance is measured relative to the center (136) of the first plate (30).

7. The mechanical counter-rotation drive according to claims 1-6, wherein motion of the first plate (30) is different from motion of the second plate (40) with a transmission ratio of 1 : 1.

8. The mechanical counter-rotation drive according to claims 1-6, wherein motion of the first plate (30) is different from motion of the second plate (40) with a transmission ratio that is different from 1:1.

9. The mechanical counter-rotation drive according to claims 1-8, wherein the drive can alternatively be driven either on the first shaft (50) or the second shaft (60), in such a way that when the first shaft (50) is driving, the second shaft (60) will be driven and vice versa, i.e., when the second shaft (60) is driving, the first shaft (50) will be driven.

10. The mechanical counter-rotation drive according to previous claims, wherein two counter-rotation drives are joined into one, such that the second shaft (60) has a larger diameter than the first shaft (50) and it is derived as a hollow tube, so that the first shaft (50) passes through it and shares the axis (56, 66) of rotation with both shafts, which causes the counter-rotation of the second shaft (60) around the first shaft (50) which in such a design passes through the whole assembly.

11. The mechanical counter-rotation drive according to previous claims, wherein vibrations are canceled out which are result of the uneven distribution of mass of a single first plate (30), where the first plate (30) and the corresponding eccentric portion (70) are doubled by design such that these two first plates (30) have the opposite distribution of mass.

12. The mechanical counter-rotation drive according to previous claims, wherein two counter-rotation drives are joined into one, such that there are two first plates (30) with two eccentric parts (70) and two second plates (40) are joined by design into one assembly and counter-rotation is transferred by a rigid connection outside the housing to a disk or cylinder that rotates in the opposite angular direction (66) with respect to the angular direction (55) of rotation of the first shaft (50), and the shaft extends through the whole assembly.

13. A compressor for a gas turbine engine, comprising: a plurality of stationary compressor blades; and a plurality of rotating compressor blades, wherein the rotating compressor blades are operatively connected to a mechanical counter-rotation drive comprising; a support structure that remains stationary with respect to the mechanical drive and providing a structural point of attachment for the mechanical drive; a first driving shaft that provides a drive torque and has an eccentric portion; a second shaft, having a same axis of rotation as the first shaft, functioning as a driven shaft and rotating in a second angular direction of rotation that is opposite to a first angular direction of rotation of the first shaft; a first plate having a plurality of lobes and operationally connected with the eccentric portion of the first driving shaft and having a center that is not aligned with an axis of rotation of the first and second shafts and rotates eccentrically with respect to the axis of rotation; a plurality of first pins operationally connected to the support structure and arranged such that a portion of a perimeter of the first plate is in rolling contact with the first pins and such that the arrangement causes the first plate to move with an angular direction of rotation which is opposite to the angular direction of rotation of the first shaft; a plurality of second pins which are operationally connected to the first plate or are its constitutive parts; and a second plate having a plurality of lobes and is operationally connected with the first plate in such a way that a perimeter of the second plate is in rolling contact with the second pins of the first plate producing a rotation of the second plate in the same angular direction of rotation as the first plate, wherein the second shaft is operationally connected to the second plate or is a constitutive part of the second plate, and is driven by the second plate.

14. The compressor as claimed in claim 13, wherein the counter-rotation drive comprises a second counter rotation drive joined to produce a new counter-rotation drive, such that there are two first plates and two corresponding eccentric parts and the second plates are by design joined into one assembly and counter-rotation is transferred by a rigid connection outside the housing to a disk or cylinder that rotates in the opposite angular direction with respect to the first shaft, and the shaft extends through the whole assembly.

15. The compressor as claimed in claim 14, wherein the rotating compressor blades are attached to the disc.

16. The compressor as claimed in claim 14, further comprising a bladed disk not having the counter- rotation drive and arranged to at least one bladed disk having the counter- rotating drive.

17. The compressor as claimed in claim 13, wherein the magnitude of the angular rotation of the drive torque is reversed with a transmission ratio of 1 to 1.

18. The compressor as claimed in claim 13, wherein the magnitude of the angular rotation of the drive torque is reversed with a transmission ratio different from 1:1.

19. The compressor as claimed in claim 13, wherein two counter-rotation drives are joined into one, such that the second shaft has a larger diameter than the first shaft and is hollow with the first shaft passing through the second shaft, the first and second shafts sharing a common rotational axis, which causes the second shaft to rotate around the first shaft, and the first shaft passes through the whole assembly.

20. Reduction system as claimed in claim 12, wherein the counter rotation drive is used for RPM reduction different from 1 to 1 ratio.

21. Reduction system as claimed in claim 12, wherein the counter rotation drive is used as a torque converter of the initial parameters.

22. Mechanizm as claimed in claim 12, wherein the counter rotation drive is used for precise angular movement.