WO2007094693A1

WO2007094693A1 - Mechanical device for energy conversion

Info

Publication number: WO2007094693A1
Application number: PCT/PT2007/000010
Authority: WO
Inventors: João Miguel VIEIRA CAEIRO DIAS ANTUNES
Original assignee: Vieira Caeiro Dias Antunes Joa
Priority date: 2006-02-17
Filing date: 2007-02-09
Publication date: 2007-08-23
Also published as: PT103437A; PT103437B

Abstract

The present invention refers to a mechanical device for energy conversion, that convert forces produced by an oscillation source (11) over a second annular body (3) making it oscillate, into a torque of the same body around its own axle (Z2). This torque is produced by the tangential component of the reaction forces (Rit, R3t) exerted by the first annular body (1) and by the optional third annular body (6) over the oscillating second annular body (3) due to the non slipping contact between peripheral regions (2, 4, 5, 7) of the annular bodies (1, 3, 6). The rotation of the second annular body (3) is then transferred to a shaft (9) through an angular coupling device (10).

Description

DESCRIPTION

"MECHANICAL DEVICE FOR ENERGY CONVERSION"

Technical Field

The present invention relates to a mechanical device for energy conversion that transfers mechanical power between an oscillating annular body with or without precession or rotation motion to an output rotating shaft. The mechanical energy supply to produce the oscillation of the oscillating annular body depends of the embodiment application type.

Between the possible applications they are mentioned:

1 A speed reducer with higher performance than conventional speed reducers where the oscillation of the oscillating annular body is controlled by an input shaft guiding the oscillation.

2 A piston machine where the oscillation of the oscillating annular body is controlled with mechanical connection means (such as connecting rods) to pistons.

3 An electromagnetic motor-generator where the oscillation of the oscillating annular body is controlled by electromagnetic means, having the oscillating annular body a permanent magnet and the other annular bodies electromagnetic coils for magnetic induction.

Background of the Invention

There is a permanent demand of simpler mechanical solutions, looking for the reduction of mechanical components complexity and dimensions and the increase of mechanic systems efficiency. This invention describes a new mechanical principle that can be applied to many complex systems simplifying them and increasing their efficiency. The mechanical principle describes the conversion of concentrated or distributed forces, produced by a source of oscillation through mechanical means (for example a shaft with an inclined bearing, with low torque and high rotating speed or pistons and connecting rods) , or electromagnetic means (making use of permanent magnets and/or electromagnetic coils with a rotating magnetic field) or other means, and acting over an oscillating annular body, into the rotation of a shaft having a high torque and low rotational speed. This device, because of its mechanical working principle, has zero backlash and very low friction losses. This way mechanical power transfer is maximized. This invention also permits the development of speed reduction systems with reversible rotation and continuous variable speed reductions. This invention allows new mechanical designs with machines having slim and small annular shafts and bodies . Discussion of Prior Art

The great inconveniences of prior art mechanical energy- conversion devices are basically connected to:

- necessity to conceive high dimension mechanisms to reach the end they are build for

- low power transfer due to friction losses, existence of backlashes

- difficulty of calorific energy dissipation produced by the conversion process.

1 Current speed reducers are based on cylindrical gears, bevel gears, worm gears, helical gears, herringbone gears, planetary gears, epicyclic gears or others. Common problems in speed reducer mechanisms using prior art technology are high power transmission losses due to friction, the existence of non zero backlash specially in high precision mechanisms, the difficulty to produce high speed reduction ratios in only one gear stage and the mechanic fragility of devices when used in high power transmissions. Common problems in planetary or epicyclic gear systems are tip interference and limited contact between the teeth of the gears.

Examples of such systems are described in U.S. Pat. No. 5,505,668, issued to Boris A. Koriakov-Savoysky, Igor V. Aleksahin, Ivan P. Vlasov on Aug. 2, 1994; a speed reducer in U.S. Pat. No. 0145049, issued to Detlef Axmacher, Massimiliano Gasparro, Dirk Neubauer, Nachrodt- Wiblingwerde, Pachan, Pfuetzenreuter, Markus Wilke on May 20, 2003; another speed reducer in WO03042580, issued to Tom Transmission Systems and Stanovskoy Viktor Vladimirovic on May 22, 2003.

2 On the other hand, current piston machines use crankshaft systems connected to pistons with connection rods . One aspect of these machines is the fact that when a constant torsional force is applied to the crankshaft, the resulting force in the piston is variable with the crankshaft angle, obtaining a mechanical power transfer function between the piston and crankshaft also quite variable. Due to the mechanic connection type, a high speed rotation of the crankshaft compared to the displacement speed of the pistons is achieved, what will not be always desirable .

Examples of similar systems that do not exhibit the same principle described here can be consulted in U.S. Pat. No. US2004165996, issued to Lavorwash S P A (US) on August 26, 2004; U.S. Pat. No. US2004165996 , issued to Lavorwash S P A (US) on August 26, 2004; U.S. Pat. No. US2005186085 , of the inventor Galba Vladimir (SK) on August 25, 2005;

3 Common problems of electromagnetic motor-generators are the necessity to use speed reducers so that low speed and high torque can be obtained. Other problems are the 1-arge device sizes when the speed reducer is used, the limited electromagnetic flux area and the difficulty of heat dissipation in the conversion process. Invention summary

The current patent refers to a new mechanical energy- conversion device that is far from the prior art technology because it uses an oscillating annular body system has a mean to transfer mechanical energy with higher efficiency. This mechanical working principle is used in several embodiments resulting in new solutions and solving existing problems of prior art technology.

1 The proposed device solves the problem of power transmission losses due to friction, has the advantage of having zero backlash especially for precision mechanisms, allow high reduction ratios in a single gear stage, allow the development of structural resistant mechanisms when used in high mechanical power transmissions and solves the tip interference and the limited teeth contact even when the number of gear teeth difference is only one (independently of tooth profile) . This way friction losses and backlash are minimized and torque and power transmission is maximized. To accomplish this, power is directly supplied to oscillate an oscillating annular body. This device can be used in machines that need high reduction gear ratios with high power and torque transmissions, in reductions of high precision shafts or others .

2 For piston machines, replacing the crankshaft with an oscillating annular body as described in this patent results in a system that has a more continuous mechanical power transfer function between the pistons and the output shaft . Piston machines that need reduction gears beneficiate with this technology, reducing the size of the machine and increasing efficiency compared with traditional systems .

This device can be used in piston machines that need speed reduction and have high power and torque transmissions .

3 With this new concept the electromagnetic motor- generator is integrated in the speed reducer avoiding power losses of further outside speed reducers. Because of annular body format, low volume and high electromagnetic flux area can be obtained with high calorific energy dissipation.

The electromagnetic motor-generator device is capable of high load starts and with control means can be used as servo mechanism actuator. This device can be applied in machines that need small electric motors with high torque output. It can also work as electromagnetic generator with adequate control means .

Working principle

As it can be seen from figures 1 and 2, a perspective and a frontal view of three annular bodies 1, 3 and 6 are represented in the XYZ Cartesian system describing geometric relations and forces actuating in the second annular body 3 that oscillates. The arrangement of annular — 1 —

bodies 1 and 6 allow a stable equilibrium of the actuating forces over the oscillating second annular body 3. The figure 3 represents the same three annular bodies 1, 3 and 6 in a planar diagram of a toroidal surface resulting from the revolution of the circumference of figure 2 around Z axle, the distributed forces σ_± and σ₃ actuating over the oscillating second annular body 3 and the tangential reaction forces R_lt e R_3t. The first annular body 1 makes contact with an oscillating second annular body 3 without slipping, over the primitive line IpI in the position of a reaction force with radial Ri_r, tangential R_lt and vertical R_lz components acting on second oscillating annular body 3. The second oscillating annular body 3 contacts the third annular body 6 without slipping, over the primitive line Ip2 in the position of a reaction force acting on second oscillating annular body 3 with radial R_3r/ tangential R_3t and vertical R₃₂ components. The angular speed rotation of the bodies 1, 3 and 6 are represented by OJ₁ around Z axle, ω₂ around Z₂ axle, and ω₃ around Z axle respectively. The forces F₁ and F₃ are the sum of distributed forces θχ and σ₃ respectively, applied to the second oscillating body 3, producing a torsional force around its own X₂ axle. The distributed forces O₁ and σ₃ are produced by a source of oscillation that make the second body 3 oscillate with angular velocity ω_F around the vertical Z ' axle. The referential with axles X₂, Y₂, and Z₂ rotate around Z axle coherently to the distributed forces σ_% and σ₃. The forces R_lr and R_3r are radial components that guide the oscillating annular body 2 in the planetary motion when ø_pi_anet_ary is not null. For 0_pia_netary nu11 there is no planetary motion and forces Rχ_r and R_3r are null .

The forces R_it and R_3t are the tangential components due to the non slipping reaction of the first annular body 1 and the third annular body 6 respectively and are responsible for the output torque in the oscillating annular body 3 around Z₂ axle. The non slipping reaction between annular bodies can be obtained in different ways depending from the considered embodiment. The presented embodiments use gearing teeth's to avoid slipping. This invention pretends that other forms of non slipping be considered, such as the utilization of drag between contact surfaces, use of specific lubricants that provide more drag, use of belts or chains between the annular bodies, the use of electromagnetic forces, intermolecular forces or a combination of several.

The forces Ri_Z and R_3Z are vertical reaction components and contribute indirectly to avoid slipping between annular bodies 1 and 6 and the second annular body 3. These forces are directly proportional to the drag and function of the drag coefficient between surfaces and directly proportional to gearing pressure in the case of embodiments with gear teeth's.

The second oscillating annular body 3 with diameter øoscxiiator has peripheral regions making angles Ot₁ and Ot₃ with X₂ axle, defining the primitive lines IpI and Ip2 and where the angles are inside the interval [-90°, 90°] . The oscillating annular body 3 has an oscillating and precession motion around point A and rotation around Z₂ axle. The motion is a compound movement with three components, it oscillates inside a sphere with diameter ø_osciii_ator that has a vertical axle Z₂ making an inclination angle γ with Z axle. The oscillating annular body 3 rotates also around itself in Z₂ axle and the sphere has simultaneously a planetary movement with diameter 0_pianetary around Z axle. The composition of the movements results in a torus surface revolution where all three bodies 1, 2 and 3 are circumscribed.

Point A is the intersection point between Z₂ axle and Z axle and has distance z_A from XY plane. Point A is the fixed point vertex where the oscillating annular body 3 moves. This point is also the rotation center point of a cardan, double cardan or bellow to transfer the rotation of annular body 3 into a rotating shaft around Z axle. The distance Δz₁₃ is a Z axle measure between annular bodies 1 and 6 in the intersection of the primitive line IpI and Ip3 and the sphere of diameter 0_Osciiiator-

The figure 4 represents a diagram of blocks with the working principle of the device where the same three annular bodies 1, 3 and 6 of figures 1, 2 and 3 are represented under the form of blocks . The blocks communicate between themselves through bidirectional arrows representing mechanical or other link means where energy exchanges exist. The set of the three annular bodies 1, 3 and 6 is called Mechanic Modulator where the bodies contact between them without slipping in peripheral regions 2 and 4 in annular bodies 1 and 3; and peripheral regions 5 and 7 for annular bodies 6 and 3; due to reaction forces Ri_t and

Rat-

The Mechanic Modulator modulates the rotation of the second annular body 3 with annular bodies 1 and 6 because there is no slipping between bodies and because the oscillating and precession motion of annular body 3 is forced by the distributed forces Oχ and σ₃, oscillating with angular velocity ω_F produced by connecting mean 13 to the Oscillation Source, being this one connected to exterior through connection means 17. The Mechanic Modulator is compound by Shaft 8 having at least the first annular body 1 and the Shaft 8' having at least the third annular body 6 and that transmit the rotation to exterior with connection means 15 e 15' with angular speeds ωi and ω₆ respectively swapping Mechanical Energy of Shaft 8 and Mechanical Energy of Shaft 8' with exterior. The Mechanic Modulator transmits the motion of the second annular body 3, with oscillation, precession and rotation ω₂ to the block called Mechanic Demodulator through connection means 12 to the angular coupling device 10.

The block Mechanic Demodulator filters the oscillating and precession motion from the Mechanic Modulator through the angular coupling device 10 to the shaft of the demodulator 9 through connection means 14, transmitting only the rotation ω₂ of the second annular body 3. The angular coupling device 10 can be a simple cardan, a double cardan, a flexible bellow, an elastic coupling, a gearing coupling, blades coupling, drum coupling, elastic shafts subject to flexion or another similar device. The rotation of the demodulator shaft 9 is then transmitted to exterior with connection means 16, being available the exchange of Mechanic Energy of Demodulator Shaft with the exterior.

In general form the Oscillation Source can be mechanic (as is the case of the speed reducer embodiment) , of internal combustion (for the piston machine embodiment) , electromagnetic (for the electromagnetic motor-generator embodiment), hydraulic, pneumatic, aerodynamic, hydrodynamic, chemical, or a combination of several of these sources of oscillation, as far as it produces the mechanical oscillation with or without precession of the second annular body 3. It depends of the considered embodiment . This Oscillation Source can be powered by Energy came from the exterior or else supply Energy to the exterior, this will depend from the considered embodiment and the mode it is working. In the most general form it is possible to make energy and power flow through all directions pointed by the large arrows represented in figure 4.

The hatched block indicates the Unit of Invention.

The following equations are obtained using geometric formulas to determine angular speed relations between annular bodies 1, 3 and 6 and the angular oscillation speed ω_F of the annular body 3 produced by the oscillation source. It is assumed ω_F as the input angular speed and ω₂ as the output angular speed of the system. The angular velocity of annular body 1 is set to zero ωχ=Q to determine the reduction factor of the system. The equations still allow to distinguish and to isolate particular cases of the models characterized by possessing one or more restriction conditions to the model with General Functioning.

For the General Functioning, the perimeters in the eri heral re ions of the annular bodies are given by:

For the General Functioning, the reduction factor of the angular speeds between ω_F and ω₂ is given by:

For the General Functioning, the distances zA and Δzl3 are given by:

The variables a_lt α₃, γ, 0_Osciiiator and 0_pia_netary define all the geometry and angular speed relations of the annular bodies . One or more than one of those variables can be controlled mechanically to obtain a continuous variable speed reduction between the rotating forces and the angular speed of any of the three annular bodies, with or without angular speed reversing.

For the embodiments in this patent some restrictions are

For the embodiments in this patent there is no inversion of the output angular speed, the reduction factor between ω_F and ω₂ depends only of a e γ variables and is given by: Reduction Factor ω₂/ω_P for Condition 1

(D₂ cos(α) .1 ω_F cos(γ + a)

For other particular cases of embodiments not presented in this patent are imposed other restrictions to the General Functioning. The particular case 4 permits the compound motion circumscribed in a toroidal surface of the second annular body 3 :

For this particular case the reduction factor depends only

The use of gears in the peripheral regions of the first, second and third annular bodies described in this patent imposes an additional condition that guarantees that the perimeters P₁/ p_3/ p₂i and p₂₃ are a multiple whole number of the thickness of the teeth's. The variables ce_i; α₃ and γ are further conditioned by:

The direction of rotation of the annular bodies varies with the alteration of the perimeter of the trajectory of contact between the annular bodies . The angular speed rotation ω_F, ω_lf ω₂ and ω₃ are considered positive in the direction of the arrows drawn in figures 1 and 2 getting the following relations:

For models described in this patent the torques applied to the second annular body are calculated with static balance: Torque in 2nd Annular Body- around X₂ axle due to Fi and F₂ M_X2=0_o,_dπatar(F₁+F₂)∞s(y) Forces

Tangential reaction forces due to non slipping between annular

bodies

Torque in 2nd Annular Body around Z₂ axle transmitted to M«-e>~,fr+F, w+2* demodulator shaft

The following table shows the relation between the variables Qj₁, α₃, γ for all described embodiment models and

Where 0_planet_ary=0 :

Other particular cases where no embodiment models are presented can be resumed under the following conditions:

Particular Case 5 :

The annular body 6 is eliminated and the device is reduced to two annular bodies with the consequent loss of balance of reaction forces in the oscillation of the annular body 3 but increasing simplicity.

Particular Case 6 :

Increasing the complexity of the system it is possible to use more than one oscillating annular body beyond annular body 3 between annular bodies 1 and 6 allowing as many simultaneous angular speeds as the number of oscillating annular bodies. In this case oscillating annular bodies meet ones overlapping on the others, each one with its inclination angle (γ) , with the respective angular couplings and demodulators shafts. The contact without slipping between the oscillating annular bodies will be carried through the same way of annular bodies 1, 3 and 6.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention will be subsequently described with the help of the figures representing, without any limitative characteristic :

The Figure 1, a perspective view of three annular bodies that explain the General Functioning of the Mechanic

Modulator;

The Figure 2, the front view cut of the three annular bodies that explain the General Functioning of the Mechanic

Modulator;

The Figure 3, a diagram with the toroidal surface represented in a plane with the three annular bodies explaining the forces distribution in the oscillating annular body 3 and the working principle of the mechanic modulator;

The Figure 4, a block diagram explaining the mechanic interactions and energy swaps between components of the device as well as its working principle; The Figure 5 represents a perspective view of the Speed

Reducer with several body cuts showing the internal parts and assembly between them;

The Figure 6 represents a front view cut of the Speed

Reducer representing internal parts and assembly between them;

The Figure 7, a diagram with the spherical surface represented in a plane with the three annular bodies explaining the forces distribution in the oscillating annular body 103 of the mechanic modulator in the Speed

Reducer;

The Figure 8, a block diagram explaining the mechanic interactions and energy swaps between components of the

Speed Reducer as well as its working principle;

The Figure 9 represents a perspective view of the Speed

Reducer components assembly;

The Figure 10 represents a perspective view of the Piston

Machine with several body cuts showing the internal parts and assembly between them. The Piston Machine is not completely represented because the drawing only puts in evidence the working parts related to this invention and missing the actuators control for the valves, the spark ignition system, the intake injection system and the exhaust system, all of them interconnected by the gearing means to exterior 224 and fixed to the motor body 209;

The Figure 11 represents a front view cut of the Piston

Machine representing internal parts and assembly means.

This figure misses the same parts as Figure 10 for the same reasons stated before . The Figure 12, a diagram with the spherical surface represented in a plane with the three annular bodies explaining the forces distribution in the oscillating annular body 203 of the mechanic modulator in the Piston

Machine ;

The Figure 13, a block diagram explaining the mechanic interactions and energy swaps between components of the

Piston Machine as well as its working principle;

The Figure 14 represents a perspective view of the Piston

Machine components assembly;

The Figure 15, a perspective view of the Electromagnetic

Motor-Generator with several body cuts showing the internal parts and assembly between them.

The Figure 16 represents a front view cut of the

Electromagnetic Motor-Generator representing internal parts, the electromagnetic arrangement of coils and their electric currents and the magnetic poles of coils and magnets .

The Figure 17, a diagram with the spherical surface represented in a plane with the three annular bodies explaining the forces distribution in the oscillating annular body 303 of the mechanic modulator in the

Electromagnetic Motor-Generator;

The Figure 18, a block diagram explaining the mechanic interactions and energy swaps between components of the

Electromagnetic Motor-Generator as well as its working principle;

The Figure 19 represents a perspective view of the

Electromagnetic Motor-Generator components assembly; The following table groups the figures by type of representation :

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

As it can be observed in the figures, the present invention describes an energy conversion mechanical device that convert forces produced by a source of oscillation (11, 135, 211 and 213, 311 and 312) over an oscillating second annular body (3, 103, 203, 303), oscillating it, into a torsional force in the same body around its own axle (Z₂) . The torsional force is produced by the tangential reaction forces component (Rχ_t, R3t) due to the first annular body (1, 101, 201, 301) and by the third annular body (6, 106, 206, 306) over the oscillating second annular body (3, 103, 203 , 303) due to the non slipping contact surface between peripheral regions (2, 102, 202, 302; 4, 104, 204, 304; 5, 105, 205, 305; 7, 107, 207, 307) of the annular bodies (1, 101, 201, 301; 3, 103, 203, 303; 6, 106, 206, 306) . When the perimeters of the annular bodies along their peripheral contact regions are different, a speed reduction is obtained between the oscillating angular speed of the second annular body (3, 103, 303) due to the forces produced by the oscillation source and the rotation of the second annular body (3, 103, 303) or the rotation speed of the modulator shaft (208) . In the oscillating annular body of the speed reducer and the electromagnetic motor- generator (103, 303) the rotation is transferred to the demodulator shaft (109, 309) with coincident axle of the first and third annular bodies (101, 301 and 106, 306) trough a flexible bellow coupling element (110, 310) . In the case of the Piston Machine a cardan ring 210 is used to prevent the rotation of the oscillating annular body 203 connected to the motor body 209 that works as a fixed Demodulator Shaft.

The oscillating second annular body 3 oscillates around a fixed center point A, rotates around itself and has a planetary precession motion around point A. Due to the restrictions imposed to the embodiments when compared to the General Functioning, the oscillating annular bodies (103, 203, 303) don't have planetary motion, neither precession around point A, they just oscillate around point A. The oscillating annular bodies (103, 303) rotate around themselves while the annular body (203) only oscillates.

The annular bodies (1 and 6, 101 and 106, 201 and 206, 301 and 306) having peripheral regions (2 and 7, 102 and 107, 202 and 207, 302 and 307) contact the oscillating annular bodies (3, 103, 203, 303) having peripheral regions (4 and 5, 104 and 105, 204 and 205, 304 and 305) in a non slipping rotating contact surface along the trajectory of the peripheral regions . The contact surface shape and material are designed to maximize friction in the tangential direction between the oscillating annular body (3, 103, 203, 303) and the annular bodies (1 and 6, 101 and 106, 201 and 206, 301 and 306) so that no slipping occurs obtaining a zero backlash coupling. The forces produced by the Oscillation Source over the oscillating second annular body produce normal and tangential reaction components due to the annular bodies (1 and 6, 101 and 106, 201 and 206, 301 and 306) , corresponding to the sum of the distributed pressure forces in the oscillating annular body (3, 103, 203, 303) in the position of the contact surfaces. Those contact surfaces rotate following the peripheral regions (4 and 5, 104 and 105, 204 and 205, 304 and 305) . In the figures 5, 6, 7, 8 and 9 is represented a Speed Reducer according to this invention. The Speed Reducer preferred embodiment described in this invention consists of a mechanic speed reducer with the aspect of a slim bearing, but with input and output shafts in the place of the inside bearing shaft. The Speed Reducer has supporting means to connect to external fixed and rotatable elements.

The first annular body 101 and a third annular body 106 are mechanically fixed by means of modulator shaft fastening screws 115 for embodiment assembling purposes, and together form the modulator shaft 108. The modulator shaft 108 has first connection means 136 to an external non rotatable element. The second annular body 103 has a second peripheral region 104 and a third peripheral region 105. The first annular body 101 has first peripheral region 102 with gearing teeth's paired with second peripheral region 104 of the second annular body 103.

In the same way, the third annular body 106 has fourth peripheral region 107 with gearing teeth' s paired with third peripheral region 105 of the second annular body 103. The first peripheral region 102 and the fourth peripheral region 107 have 200 (two hundred) teeth's.

The second peripheral region 104 and the third peripheral region 105 have 201 (two hundred and one) teeth's. The oscillator shaft 135 is a fast rotatable shaft with third connection means 138 for an external rotatable element working as energy input shaft of the embodiment. The oscillator shaft 135 is assembled to the modulator shaft 108, on the first annular body 101, as a first bearing 120 with balls and inner and outer bearing races as shown in figures 3 and 4. The oscillator shaft 135 is assembled to the second annular body 103 has a third bearing 133 having its axle coincident to the second annular body 103 axle, and making a fixed angle with the oscillator shaft 135 axle.

The second annular body 103 oscillates and rotates inside the modulator shaft 108 geared by peripheral regions (102, 104, 105 e 107) with a fixed inclination angle between their axles .

The demodulator shaft 109 is a slow rotatable shaft with second shaft connection means 137 to another external rotatable element working as energy output shaft of the embodiment. The demodulator shaft 109 is assembled to the modulator shaft 108 as a second bearing 121 with balls and inner and outer bearing races as shown in figure 3 and 4, and with the axles coincident to the first bearing 120 axle .

The rotation of the second annular body 103 is transferred to the demodulator shaft 109 by means of a bellow coupling element 110 projected to be circumscribed in a spherical surface centered in point A. The bellow coupling element 110 is rigidly attached to the second annular body 103 by means of a first brass wire press-fit connection 124 and attached in the other side to the demodulator shaft 109 by means of a second brass wire press-fit connection 125. This way, the speed rotation of the oscillator shaft 135 is transferred with a speed reduction to the demodulator shaft 109 with zero backlash and high efficiency. The speed reduction factor is of 200. Two hundred complete rotations of the oscillator shaft 135 correspond to one rotation in the demodulator shaft 109.

In the block diagram of figure 8 it's possible to observe how the Speed Reducer components are interconnected. The Mechanic Modulator is constituted by the first annular body 101, the second annular body 103, and the third annular body 106. The second annular body 103 gears the first annular body 101 in peripheral regions 102 and 104 and gears third annular body 106 in peripheral regions 105 and 107, has already described before. This Mechanic Modulator block modulates the rotation of the second annular body 103 through the Oscillation Source corresponding to the oscillator shaft 135 and swapping energy through the third bearing 133. In this embodiment the first annular body 101 is connected to the third annular body 106 through modulator shaft fastening screws 115 fixed to exterior by first connection means 136. The Oscillation Source is supported and rotates through first bearing 120 to the first annular body 101 receiving Mechanic Energy of Oscillator Shaft through the third connection means 138. The Mechanic Demodulator is constituted by the bellow coupling element 110 and the demodulator shaft 109, receives mechanic energy to the bellow coupling element 110 from the second annular body 103 through the first brass wire press-fit connection 124 with rotation and oscillation motion. The demodulator shaft 109 is supported and rotates over the third annular body 106 through the second bearing 121. The Mechanic Demodulator filters the oscillation motion transmitting the rotation mechanic energy to the demodulator shaft 109 through the second brass wire press- fit connection 125 and then transmitted to the exterior through the second connection means 137. This way the demodulator shaft 109 works as a mechanic energy output shaft of the embodiment .

The filled arrows indicate the direction of the power and mechanic energy transmission, that come from the exterior to the oscillator shaft 135 then to the demodulator shaft 109 through the Oscillation Source corresponding to the oscillator shaft 135, then to the second annular body 103, then to the Mechanic Demodulator with the bellow coupling element 110 and the demodulator shaft 109. Due to the high reduction ratio of 200 the transmission of energy and power is essentially unidirectional, from the Oscillation Source to the demodulator shaft 109. The dashed line block delimits the invention unity.

In the figures 10, 11, 12, 13 and 14 is represented a Piston Machine according to this invention.

The Piston Machine preferred embodiment described herein consists of an internal combustion engine based on the same mechanical conversion principle described in this invention. The internal combustion engine has 16 (sixteen) pistons arranged in pairs of two. Each pair of pistons works together in opposite directions, pushing and pulling an oscillating annular body 203. A first annular body 201 has spiral conic gearing teeth's in the inner peripheral region 202. The first annular body 201 and an equal third annular body 206 are mechanically fixed to the modulator shaft body 225 by means of fastening screws for assembly purposes, forming the modulator shaft 208. The modulator shaft 208 has a first bearing 220 and second bearing 221 supporting this assembly to the engine body 209, allowing the rotation of the assembly and working has the mechanic energy output shaft of the embodiment . The second annular body 203 has spiral conic gearing teeth's in the second peripheral region 204 and third peripheral region 205 that gear in the first peripheral region 202 of the first annular body 201 and in" the fourth peripheral region 207 of the third annular body 206 respectively .

The spiral gearing teeth's are used to obtain soft gearing with lower noise and higher power transmission then other gears .

The second annular body 203 oscillates between the first annular body 201 and third annular body 206 with gearing contact. The oscillation is supplied by 16 (sixteen) con rods 212 that connect and transmit motion from the 16 (sixteen) pistons 211. The oscillating con rod supports 214 and the piston con rod supports 213 permit free rotation of the spherical con rods 212 ends maintaining the oscillating motion transmission.

The cardan ring 210 is a connection mean between the second annular body 203 and the engine body 209 so that the second annular body 203 can oscillate without having rotation in its own axle. The cardan 210 has 2 (two) cardan external rotation pins 219 connected to the engine body 209 and another (two) cardan internal rotation pins 222 (visible in figure 14) connected to the second annular body 203 making a 90° angle from each other.

The combustion chambers 218 are arranged around the engine body 209 aligned with pistons 211 motion. The combustion chambers 218 have intake valves 215, exhaust valves 217 and a hole for the spark ignition system 216. Intake, compression, power and exhaust cycles are controlled and synchronized with the oscillation of the second annular body 203 through the gearing means to exterior 224 having a rotating cycle sequence over all combustion chambers 218. Opposite combustion chambers 218 work in pairs, with compression and power or intake and exhaust . Consecutive combustion chambers 218, in the same engine body 209 side, work alternately with intake and power or compression and exhaust .

The spiral conic gearing of the second annular body 203 has 40 (fourteen) teeth's while the spiral conic gearings of the first annular body 201 and the third annular body 206 have both 41 (forty one) teeth's. A full rotation of the modulator shaft 208 corresponds to 40 (fourteen) complete oscillations of the second annular body 203 and 20 (twenty) full combustion cycles in each combustion chamber 218.

In the block diagram of figure 13 is possible to observe how the Piston Machine components are interconnected. The Mechanic Modulator is constituted by the first annular body 201, the second annular body 203, and the third annular body 206. The first annular body 201 gears the second annular body 203 through the first peripheral region 202 and the second peripheral region 204 so that no slipping occur between those components. The third annular body 206 gears to the second annular body 203 through the third peripheral region 205 and the forth peripheral region 207 so that no slipping occur between those components. The Mechanic Modulator block modulates the rotation of the first annular body 201 and the third annular body 206 because the rotation of the second annular body 203 is fixed due to the Mechanic Demodulator. The modulation is obtained by the Oscillation Source constituted by pistons 211 and by piston con rod supports 213 that connect to the second annular body 203 through the con rods 212 and the oscillating body con rod supports 214. The internal combustion in the combustion chambers 218 supplies the Oscillation Source with Mechanic Energy.

The Mechanic Demodulator is constituted by a coupling cardan 210 and by a fixed demodulator shaft corresponding to the engine body 209. The cardan 210 avoid the second annular body 203 to rotate through the cardan internal rotation pins 222. The cardan 210 doesn't rotate because the cardan external rotation pins 219 are connected to the engine body 209. This way the oscillation motion of the second annular body 203 is filtered and its rotation motion is avoided due to the engine body 209 being fixed by the device fixing means 223 to an external element. The modulator shaft 208 is supported and rotates over the engine body 209 through the first bearing 220 and the cardan internal rotation pins 222. The rotation of the modulator shaft 208 is obtained due to the rigid connection of this to the first annular body 201, to the third annular body 206 and the modulator shaft body 225, receiving energy that is transmitted to a exterior Load through gearing means to exterior 224 existing in the modulator shaft body 225. This way the modulator shaft 208 works as a mechanic energy output shaft of the embodiment .

The filled arrows indicate the direction of the power and mechanic energy transmission in the Mechanic Modulator, which is distributed by the two gearings without slipping in peripheral regions 205 with 207 and 202 with 204 being applied to the modulator shaft 208. The direction of power and energy transmission is essentially from the Oscillation Source to the Load due to the type of internal combustion machine . The dashed line block delimits the invention unity.

In the figures 15, 16, 17, 18 and 19 is represented a Electromagnetic Motor-Generator according to this invention.

A first annular body 301 and an equal third annular body 306 are mechanically fixed to a modulator shaft 308 by means of body fastening screws 313 for assembling purposes. These three bodies (301, 306 and 308) have internally an octagonal shape to connect to a non rotating external element .

A second annular body 303 having a second peripheral region

304 and a third peripheral region 305 oscillates and rotates between said first annular body 301 and third annular body 306.

The first annular body 301 has first peripheral region 302 with spiral conic gearing teeth' s paired with second peripheral region 304 gearing teeth's.

The third annular body 306 has a fourth peripheral region

307 with conical gearing teeth's paired with third peripheral region 305 gearing teeth's.

Spiral conic gears are used for smoother gearing with reduced noise and with higher power transmission than other types of gears .

The number of teeth's of first peripheral region 302 is equal to the number of teeth's of fourth peripheral region

307 and equals 100 (one hundred) teeth's.

The number of teeth's of second peripheral region 304 is equal to the number of teeth' s of third peripheral region

305 and equals 101 (one hundred and one) teeth's.

The second annular body 303 has oscillation and rotation guided by the modulator shaft 308 and by the two peripheral regions 302 and 307 described before.

The demodulator shaft 309 work as a mechanical energy output/input shaft of the embodiment and is compound by the first shaft bearing support 316 (supporting the outside bore of the first bearing 320) , the first shaft coupling support 317, the second shaft bearing support 318 (supporting the outside bore of the second bearing 321) and the second shaft coupling support 319 mechanically fixed by the bearings and shaft body fastening screws 315 for assembly purposes. The outside shaft body 309 has an octagonal shape to connect and transmit rotation to an external rotating element .

The first inside bearing support 322 supports the inside bore of the first bearing 320 to the first annular body 301. The second inside bearing support 323 supports the inside bore of the second bearing 321 to the third annular body 306.

The double bellow coupling element 310 is compound by the first bellow 327 and the second bellow 328 connected both to the second annular body 303 by means of the first brass wire press-fit connection 324, and to the shaft body 309 by means of the second brass wire press-fit connection 325 and the third brass wire press-fit connection 326. The bellows are projected so that they are circumscribed in a spherical surface centered in the point A. This way the second annular body 303 is allowed to oscillate maintaining a rigid rotation coupling to the demodulator shaft 309.

The oscillation of the second annular body 303 is controlled by electro-magnetic forces with rotating electromagnetic fields acting between the second annular body 303, that as a permanent magnet with radial poles as drawn in Figure 16, and the first annular body 301 and the third annular body 306, that are both magnetically induced by the external radial electromagnetic coils 311 and the internal radial electromagnetic coils 312 as drawn in Figure 16, totalizing a number of 32 (thirty two) coils. The current circulation in coils (311 and 312) is exemplified in Figure 16, the current flowing away from viewer 329 and the current flowing toward viewer 330 induce the electromagnetic poles north and south in the first annular body 301 and in the third annular body 306. The electronic switching control 331 of currents intensity and polarities is connected by electric wires to the coils (311 and 312) as drawn in Figure 16, allowing the control of the attraction and repelling of the second peripheral region 304 and the third peripheral region 305 from the first peripheral region 302 and the fourth peripheral region 307 respectively. The electronic switching control 331 is connected with electric wires to 16 (sixteen) proximity sensors 332 distributed around the first body 308 to process input information about the oscillating angle position of the second annular body 303 and feedback current to the coils (311 and 312) with the correct intensities and polarities controlling the rotation of the electromagnetic field.

To generate rotation of the demodulator shaft 309 a rotating sequence of currents intensity and polarities, is produced in coils (311 and 312) , obtaining this way an electromagnetic motor. If the demodulator shaft 309 is rotated while teeth's in peripheral regions (302, 304, 305 and 307) are engaged, then currents are induced in the coils (311 and 312) resulting in an electromagnetic generator. A servo mechanism actuator is obtained controlling the position with the electronic switching control 331.

With appropriate currents controlled by the electronic switching control 331 the second annular body 303 can have the gear mechanism disengaged to allow free rotation of the demodulator shaft 309. Disengagement is obtained with correct polarization of coils (311 and 312) inducing magnetic repealing poles into the second annular body 303, maintaining it in a center position without oscillations, just rotation. Reengagement is obtained when the rotating sequence of currents intensity and polarities is produced in coils (311 and 312) .

In the block diagram of figure 18 it's possible to observe how the Electromagnetic Motor-Generator components are interconnected. The Mechanic Modulator is constituted by the first annular body 301, the second annular body 303, and the third annular body 306 that gear trough the peripheral regions 302 to 307 and 305 to 307 as already described before. This Mechanic Modulator block modulates the rotation of the second annular body 303 granting the contact of this one to the first annular body 301 and to the third annular body 306 through the rotation of electromagnetic forces obtained from the Oscillation Source corresponding to the external radial electromagnetic coils 311 and the internal radial electromagnetic coils 312 interacting with the second annular body 303 with permanent magnetic polarization. The Oscillation Source is supplied with Electric Energy from the exterior controlled with the electronic switching control 331, using feedback information from the proximity sensors 332 attached to the modulator shaft body 333 and measuring the position of the second annular body 303. This process occurs when the embodiment works as a motor or as a generator. Electric Energy must be supplied to the coils 311 and 312 when the embodiment works as a generator so that the contact between the annular bodies is maintained, driving the oscillation of the second annular body 303. This consumed energy is quite lower then the produced energy due to the forced rotation of the mechanic demodulator transmitted to the second annular body. This forced rotation produces more oscillation of the second annular body 303 as well as induction in the coils. This way Electric Energy is transferred to the exterior driven by the electronic switching control 331.

The first annular body 301 and the third annular body 306 are fixed to the demodulator shaft 308 by the body fastening screws 313 and then fixed to an external body through the internal octagonal shape of the embodiment . The mechanic energy of the second annular body 303 is transmitted or received by the Mechanic Demodulator with the double bellow coupling element 310 being this one composed by the first bellow 327 and the second bellow 328, both sharing the power and energy transmission through the press-fit connections 324, 325 and 326 as described before. This way the oscillation motion of the second annular body 303 is filtered and the rotation is transmitted or received from the demodulator shaft 309, also making part of the Mechanic Demodulator/ with the press-fit connections 325 and 326. The external octagonal shape of the demodulator shaft 309, supported with rotation by the first bearing 320 to the first annular body 301 and by the second bearing 321 to the third annular body 306, with bearings fastening screws 314 fixing means and bearing supports 322 and 323, allows to transmit and receive energy and power to the Load, working as a mechanic energy output/input shaft of the Electromagnetic Motor-Generator.

The direction of energy and power transmission of the Electromagnetic Motor-Generator is bidirectional as the filled arrows indicate in the diagram of Figure 18. The dashed line block delimits the invention unity. Reference List for the General Functioning (figures 1, 2, 3 and 4) :

1 first annular body

2 first peripheral region

3 second annular body

4 second peripheral region

5 third peripheral region

6 Third annular body

7 fourth peripheral region

8 first modulator shaft 8' second modulator shaft

9 demodulator shaft 10 angular coupling device

11 oscillation source

12 connection mean of modulator to demodulator

13 connection mean of modulator to oscillation source

14 connection mean of angular coupling device to demodulator shaft

15 connection mean of shaft 8 to exterior 15' connection mean of shaft 8' to exterior

16 connection mean of demodulator to exterior

17 connection mean of oscillation source to exterior

X horizontal axle

Y transversal axle (direction of observer)

Z vertical axle

X₂ horizontal axle of third annular body

Y2 transversal axle of third annular body

Z₂ vertical axle of rotation of third annular body

A intersection point between Z and Z₂ axles

Z_A distance between point A to XY plane

Δ_Zi3 vertical distance between pi and P₃ lpi primitive line 1

Ip₂ primitive line 2

Pi perimeter along first peripheral region of first annular body P21 perimeter along second peripheral region of second annular body P23 perimeter along third peripheral region of second annular body p₃ perimeter along forth peripheral region of third annular body ω_F oscillating angular speed of second annular body due to Fi and F₃ forces produced by the source of oscillation coi angular speed rotation of first annular body ω₂ angular speed rotation of second annular body ω₃ angular speed rotation of third annular body γ inclination angle between Z and Z₂ axles Ot₁ angle of X₂ axle to primitive line 1 α₃ angle of X₂ axle to primitive line 2 øpianetary diameter of planetary motion ø_osciiiatordiameter of second annular body O₁ distributed forces applied to the second annular body in the direction of the first annular body produced by the oscillation source σ₃ distributed forces applied to the second annular body in the direction of the third annular body produced by the oscillation source Fi resulting force applied to second annular body due to distributed forces O₁ F₃ resulting force applied to second annular body due to distributed forces σ₃ Rir radial reaction force applied to second annular body due to first annular body Rit tangential reaction force applied to second annular body due to first annular body Riz vertical reaction force applied to second annular body due to first annular body R_3r radial reaction force applied to second annular body due to third annular body R_3t tangential reaction force applied to second annular body due to third annular body R.3Z vertical reaction force applied to second annular body due to third annular body

Mχ₂ torque around X₂ applied to second annular body M₂₂ torque around Z₂ applied to second annular body

Reference List for the Speed Reducer (figures 5, 6, 7, 8 and 9) :

first annular body first peripheral region second annular body second peripheral region third peripheral region third annular body fourth peripheral region modulator shaft demodulator shaft bellow coupling element modulator shaft fastening screws first bearing second bearing first brass wire press-fit connection second brass wire press-fit connection third bearing oscillator shaft first connection means second connection means third connection means

Reference List for the Piston Machine (figures 10, 11, 12, 13 and 14) :

first annular body first peripheral region second annular body second peripheral region third peripheral region third annular body fourth peripheral region modulator shaft engine body cardan pistons con rods piston con rod supports oscillating body con rod supports intake valves hole for the spark ignition system exhaust valves combustion chambers cardan external rotation pins first bearing second bearing cardan internal rotation pins device fixing means gearing means to exterior modulator shaft body

Reference List for the Electromagnetic Motor-Generator (figures 15, 16, 17, 18 and 19) :

first annular body first peripheral region second annular body second peripheral region third peripheral region third annular body fourth peripheral region modulator shaft demodulator shaft double bellow coupling element external radial electromagnetic coils internal radial electromagnetic coils body fastening screws bearings fastening screws bearings and shaft body fastening screws first shaft bearing support first shaft coupling support second shaft bearing support second shaft coupling support first bearing second bearing first inside bearing support second inside bearing support first brass wire press-fit connection second brass wire press-fit connection third brass wire press-fit connection first bellow second bellow current flowing away from viewer current flowing toward viewer electronic switching control proximity sensors modulator shaft body

Reference Tables

The next reference table resumes the elements references by common functionality to all embodiments preserving the same invention unity:

The next reference table resumes characteristics of the several elements of the embodiments that preserving the same invention unity allow different implementations:

Speed Electromagnetic

Block Diagram Elements General Functioning Piston Machine Reducer Motor-Generator

Non slipping surface with or Planetary

1st and 4th Spiral conical Spiral conical

Mechanic without specific bevel gears

Peripheral gears with 40 gears with 100 Modulator products for added with 200

Region teeth's teeth' s drag, gearing teeth' s teeth' s, belts, chains, electromagnetic Planetary

2nd and 3rd Spiral conical Spiral conical forces, bevel gears

Peripheral gears with 41 gears with 101 intermolecular or with 201

Region teeth' s teeth' s other, combination teeth' s of several .

The invention is not limited to the above-described embodiments; additional configurations and modifications are possible while still remaining within the scope of the following claims .

Claims

- 52CLAIMS

1. A mechanical device for energy conversion that transfers energy between the oscillating annular body with or without precession and rotation for a rotating output shaft characterized by having:

a) a first annular body (1, 101, 201, 301) having a first peripheral region (2, 102, 202, 302) that can be endowed with rotating motion around its axle;

b) a second annular body (3, 103, 203, 303) disposed above the first annular body having a second peripheral region

(4, 104, 204, 304) and being endowed with oscillating motion around point (A) , being still able to be endowed with rotation and/or precession motion and having an optional third peripheral region (5, 105, 205, 305) ;

c) an optional third annular body (6, 106, 206, 306), disposed above the second annular body that can be endowed with rotating motion around its axle; where the second annular body (3, 103, 203, 303) axle makes an angle gamma (γ) with the first annular body (1, 101, 201, 301) axle, and wherein the first peripheral region (2, 102, 202, 302) of the first annular body (1, 101, 201, 301) contact the second peripheral region (4, 104, 204, 304) of the second annular body (3, 103, 203, 303) in a non - 53 -

slipping contact surface along the primitive line (IpI) , and wherein the perimeter (pi) of the first peripheral region (2, 102, 202, 302) is different of the perimeter (p21) of second peripheral region (4, 104, 204, 304) ;

d) one or more supporting means between the first annular body (1, 101, 201, 301) and the second annular body (3, 103, 203, 303) and between the second annular body (3, 103, 203, 303) and the third annular body (6, 106, 206, 306) that allow the oscillation of the second annular body (3, 103, 203, 303) above the first annular body (1, 101, 201, 301) and the third annular body (6, 106, 206, 306) so that the first peripheral region (2, 102, 202, 302) contact the second peripheral region (4, 104, 204, 304) and the third peripheral region (5, 105, 205, 305) contact the fourth peripheral region (7, 107, 207, 307) in a rotating form along the contact surfaces without slipping in both cases;

e) being able to be connected to the first annular body (1, 101, 201, 301) as well as to the third annular body (6, 106, 206, 306) a shaft for each one (8, 8') that don't have independent rotation, or an only shaft, modulator shaft (108, 208, 308) joining the shafts (8) and (8'), or either the previous two annular bodies, shafts that interact with the rotating, oscillation and precession motion of the second annular body (3, 103, 203, 303);

f) a guiding mechanism in the first annular body (1, 101, 201, 301) and in the third annular body (6, 106, 206, 306) - 54 -

so that the second annular body (3, 103, 203, 303) can rotate, oscillate or have precession motion;

g) a demodulator shaft (9, 109, 209, 309) connected to the second annular body (3, 103, 203, 303) by an angular coupling device (10, 110, 210, 310) so that only the rotation of the second annular body (3, 103, 203, 303) is transferred to the demodulator shaft (9, 109, 209, 309) ; converting forces from the oscillation source (11, 135, 211+213, 311+312) actuating over the second annular body (3, 103, 203, 303), making it oscillate, in a rotation torque of the same body around its axle, torque obtained from the tangential force reactions exerted by the annular bodies (1 and 6, 101 and 106, 201 and 206, 301 and 306) over the second annular body (3, 103, 203, 303) due to the condition of non slipping contact surfaces of the annular bodies, resulting in an angular speed reduction of the oscillation of the second annular body (3, 103, 203, 303) produced by the oscillation source and the rotation speed of the second annular body (3, 103, 203, 303), being the torque transmitted to the demodulator shaft (9, 109, 209, 309) ;

2. A mechanical device for energy conversion, according to claim 1, characterized for being able to make use of more than one oscillating annular bodies disposed above the first annular body (1, 101, 201, 301) and that are endowed of oscillating motion around point (A) , being still able to be endowed of rotation and precession motion; - 55 -

3. A mechanical device for energy conversion, according to claims 1 and 2, characterized by the first (2, 102, 202, 302) with the second (4, 104, 204, 304) and the third (5, 105, 205, 305) with the fourth (7, 107, 207, 307) peripheral regions being in contact one with the others through primitive lines (IpI, Ip2) that are dependent of the system geometry defined by the variables α_lf CK₃, γ,

^oscillator S 0planetary/

4. A mechanical device for energy conversion, according to claims 1, 2 and 3, characterized by the contact between the annular bodies being processed by the respective peripheral regions through gearing teeth's;

5. A mechanical device for energy conversion, according to claims 1 and 3, characterized by further comprising rolling means to provide a sliding contact between the modulator shaft (8 e 8', 108, 208, 308) and the demodulator (9, 109, 209, 309) where the rolling axle is common;

6. A mechanical device for energy conversion, according to claims 1 and 3, characterized by the first annular body (1, 101, 201, 301) and the third annular body (6, 106, 206, 306) being mechanically fixed by connection means and together form a modulator shaft (8 e 8', 108, 208, 308);

7. A mechanical device for energy conversion, according to claims 1 and 3, characterized by in the case of the - 56 -

oscillating second annular body (3, 103, 203, 303) the rotation being transferred to the demodulator shaft (9, 109, 209, 309) through an angular coupling device (10, 110, 210, 310) ;

8. A mechanical device for energy conversion, according to claims 1 and 3 to 7, characterized by, when working as a speed reducer the peripheral regions (102, 104, 105 and 107) respectively of the first, second and third annular body (101, 103 e 106) being endowed of conical gearings, the second peripheral region (104) and the third peripheral region (105) with equal number of teeth's above the ones of the first peripheral region (102) and the fourth peripheral region (107), also with the same number of teeth's, rotating the second annular body (103) with oscillation motion above the first (101) and the third (106) annular bodies without rotation motion through the specified peripheral regions (102) and (107) ;

9. A mechanical device for energy conversion, according to claim 8, characterized by, the source of oscillation being an oscillator shaft (135) that produce the oscillation of the second annular body (103) through an inclined bearing

(133) in the oscillator shaft (135) that transmits distributed forces and by the demodulator shaft being constituted by at least one bellow that connect the second annular body (103) to the demodulator shaft (109) and being rigidly connected to the second annular body (103) by connection means (124) and to the demodulator (109) by - 57 -

connection means (125) , so that the rotation of the oscillator shaft (135) be transferred with reduced speed to the demodulator shaft (109) ;

10. A mechanical device for energy conversion, according to claims 1 and 3 to 7 , characterized by, when working as a piston machine, the second annular body (203) being endowed with gearing conical teeth' s in the second and third peripheral regions (204 and 205) that gear with first peripheral region (202) of first annular body (201) and fourth peripheral region (207) of the third annular body (206) oscillating said second annular body (203) between the said first and third annular bodies (201 and 206) with contact and gearing, bodies (201 and 206) that are endowed with rotation, while the second annular body (203) is endowed with oscillation without precession and without rotation;

11. A mechanical device for energy conversion, according to claim 10, characterized by the oscillation being supplied by connecting elements (212) , con rods that interconnect and transmit the piston motion (211) to the second annular body (203) maintaining the transmission of the oscillating motion, being the combustion chambers (218) placed in lathe of the engine (209) and aligned with the piston motion;

12. A mechanical device for energy conversion, according to claim 10 and 11, characterized by the cycle of intake, compression, power and exhaust being controlled and - 58 -

synchronized with the oscillation of the second annular body (203) through gearing means to exterior (224) having cyclic rotation over all the combustion chambers (218) ;

13. A mechanical device for energy conversion, according to claim 10, 11 and 12, characterized by the peripheral regions (202 and 207) of the first and third annular bodies (201 and 206) having a smaller number of teeth's than the peripheral regions (204 and 205) of the second annular body (203) and by the first (202) and the fourth (207) being endowed with equal number of teeth's and the second (204) and third (205) peripheral regions also with equal number of teeth's.

14. A mechanical device for energy conversion, according to claims 1 and 3 to 7, characterized by, when working as a electromagnetic motor-generator, the second annular body

(303) with the second and third peripheral regions (304 and 305) oscillate and rotate without precession motion between the first and third annular bodies (301 and 306) that are maintained without rotation.

15. A mechanical device for energy conversion, according to claim 14, characterized by, the first annular body (301) with the first peripheral region (302) being endowed with a gear having spiral teeth' s that gears with the gear having spiral teeth's of the second peripheral region (304), while the third annular body (306) with its peripheral region - 59 -

(307) being endowed with a gear with spiral teeth's that gears with the gear in the third peripheral region (305) ;

16. A mechanical device for energy conversion, according to claims 14 and 15, characterized by the peripheral regions

(302 and 307) of the first and third annular bodies (301 and 306) present a smaller number of teeth's than the peripheral regions (304 and 305) of the second annular body

(303) and by the first (302) and fourth (307) being endowed with equal number of teeth's and the second (304) and third

(305) peripheral regions also with equal number of teeth's;

17. A mechanical device for energy conversion, according to claim 14, characterized by, the oscillation of the second annular body (303) being able to be controlled by electromagnetic forces;

18. A mechanical device for energy conversion, according to claim 17, characterized by, the second annular body (303) being endowed of permanent magnets with radial poles and the first and third annular bodies (301 and 306) being both magnetically induced by external and internal electromagnetic coils (311 and 312) integrated radially in the annular bodies (301 and 306) , being the disposal of the magnetic axle of each induced field, a magnet (311 and 312) , perpendicular to the first and fourth peripheral regions (302 and 307) ; - 60 -

19. A mechanical device for energy conversion, according to claims 14 to 18, characterized by, the mechanic demodulator being constituted by two bellows (310) that connect the second annular body (303) to the demodulator shaft (309) ;

20. A mechanical device for energy conversion, according to claims 14 to 19, characterized by, the modulator shaft

(308) being connected to the demodulator shaft (309) by rolling means (320 and 321) and support means;

21. A mechanical device for energy conversion, according to claims 14 to 20, characterized by, the bellows (327 and 328) being rigidly fixed to the second annular body (303) and to the demodulator (309) respectively through fixing means (324) and fixing means (325 and 326) , being the electromagnetic forces produced by rotating electromagnetic fields converted to a rotation with reduced speed to the demodulator shaft (309) ;

22. A mechanical device for energy conversion, according to claims 14 to 21, characterized by, the synchronization between the oscillation of the second annular body (303) and the rotating electromagnetic fields induced by the coils (311 and 312) being controlled by an electronic switching control (331) being for this used means (332) to measure the relative position between the coils (311 and 312) and the contact region of the peripheral regions (302) with the (304) and the (305) with the (307) ; - 61 -

23. A mechanical device for energy conversion, according to claim 1, characterized by the angular coupling device (10, 110, 310) being constituted by one or more bellow couplings circumscribed in a spherical surface centered in point A that may also work as supporting means for the oscillating annular body (3, 103, 303) allowing it to oscillate;

24. A mechanical device for energy conversion, according to claims 1 and 3 to 7, characterized by, when working as a electromagnetic motor-generator the oscillation of the second annular body (3, 303) being able to be controlled by electromagnetic forces where the first annular body (1, 301), the second annular body (3, 303) and the third annular body (6, 306) are constituted by permanent magnets or electromagnetic coils having at the same time gearing teeth' s ;