BR112020012686B1 - MECHANISM FOR TRANSFORMING RECIPROCAL MOVEMENT INTO ROTATIONAL OR VICE VERSA AND APPLICATIONS THEREOF - Google Patents

Abstract

Mechanism for transforming reciprocal to rotational motion or vice versa, and mechanism applications Mechanism for transforming rotation to reciprocating motion, or vice versa, comprising a first annular component (1) and a second annular component (3) coaxially located, the first beside the second , along a longitudinal axis (ÓÓ), wherein both are able to rotate around the longitudinal axis and to reciprocate along the longitudinal axis, wherein side A of the first annular component (1) adjacent to the second annular component (3) is in continuous contact, in at least one point, with the neighboring side Ga of the second annular component (3), such that the second annular component (3) is able to rotate relative to the first annular component (1) in continuous contact in at least one point with the adjacent side (A) of the first annular component (1), wherein the contacting sides are undulated surfaces (ó, Ga), such that if the first annular component (1) and the second annular component (3) are forced into rotational motion relative to each other, remaining at the same time in continuous contact, then every point of the undulated surfaces (ó, Ga) will trace, relative to the other, an undulated trajectory and at the same will also execute, relative to the other, reciprocating motion. Figure 1.

Description

001 The invention relates to a mechanism for transforming reciprocal movement into rotational or vice versa, according to claim 1. It also refers to applications for the mechanism, such as in fluid flow control valves, in piston engines , such as motors or pumps / compressors, in automation systems as well as in clutches, differentials, rotational speed increase-reduction / reciprocity devices and electromechanical pairs in power generators / electric motors.

002 The most well-known and common straight-line reciprocal for rotational motion transformation mechanism is the piston - piston rod - crank mechanism. It finds wide application in piston engines (engines or pumps/compressors) generally operating with air, water (liquid or vapor), oil and fuels in liquid or gaseous state (e.g. hydrocarbons, hydrogen, etc.). Flow control of each working fluid is achieved by valves of various types opening and closing using many different ways or mechanisms (e.g., gravity, springs, rods, camshaft, etc.).

003 A serious disadvantage of the piston - piston rod - crank mechanism, as well as engines based on it, is the complexity and large number of moving parts. The same also applies to kinematic properties relating to the position, speed and acceleration of moving parts, as well as vibrations caused by developing inertial forces. This is why balancing the mechanism is essential; however, balancing does not completely solve the problem due to the remaining higher order harmonics. Furthermore, in ICEs (Internal Combustion Engines), a disadvantage of the mechanism also includes the inability of the piston to rest at TDC (Top Dead Center) and BDC (Bottom Dead Center) for a certain period of time, so that the combustion to improve and efficiency to increase, as well as to allow adequate time for the sweeping/washing of exhaust gases from the cylinders to occur in two-stroke engines respectively.

004 The present invention refers to a simple mechanism for transforming rectilinear reciprocating movement into rotational, or vice versa, without crankshaft and piston rod, and can also provide the possibility of delaying the inversion of movement in extreme positions of reciprocity (TDC and BDC). At the same time, it allows the provision of a valve configuration with simple ports for fluid flow control. It also refers to products that may incorporate said mechanism and/or valve configuration with simple openings, such as, and piston engines (engines or pumps/compressors), clutches, differentials, rotational speed increase-reduction device/ reciprocity, electromechanical pairs in power generators/electric motors and automations.

005 According to the invention, a mechanism is proposed for transforming reciprocal motion into rotational, or vice versa, including a first annular component and a second annular component coaxially mounted on the first adjacent to the second along a longitudinal axis, wherein both are capable of rotating about the longitudinal axis and alternating along the longitudinal axis, wherein the side of the first annular component adjacent to the second annular component is in continuous contact, at at least one point, with the neighboring side of the second annular component, wherein the contact sides are smooth wavy surfaces formed as a locus of rays passing through smooth wavy curves of the outer cylindrical surface of the first and second annular components, beginning at their outer surface and ending at their inner surface, being characterized by n (natural number Φ 0 ) repeating pairs of ridges and valleys, wherein said ridges/valleys are symmetrical with respect to the level defined by the highest/lowest point of the ridge/valley (respectively) and the longitudinal axis.

006 According to the invention, the crests of the corrugated surface of the first annular component may be in contact with the crests of the corrugated surface of the second annular component and in this position the contact points are located in a plane perpendicular to the longitudinal axis, relative to the which the wavy surfaces of the first annular component and the second annular component are symmetrical.

007 Additionally, the crests of each rippled surface are smaller than the geometrically similar valleys with a similarity ratio of 1:3, so that when the crests enter each other's valleys, the edges of the ridge come into contact with the At the lowest point in the valleys of the opposite corrugated surface, free space remains between the corrugated surfaces, resulting, when lubricated, in achieving friction and minimizing wear due to dynamic lubrication.

008 With the proposed mechanism, if the first annular component and the second annular component are forced into a rotational movement relative to each other, while remaining in continuous contact, then each point of the wavy contact surfaces will trace, in relation to the other, a wavy trajectory and will execute at the same time, in relation to the other, a reciprocating movement n-times the frequency, where n is the number of crests/valleys, of the corresponding rotational movement frequency, between a TDC (Top Dead Centre) and a BDC (Bottom Dead Centre), this relative movement being executed by each component firmly connected to one of the annular components, while each component, for example a piston, connected to one of the annular components, in such a way that this connected component is free not to follow the rotation of the component to which it is connected, it performs reciprocating motion only relative to the other annular component so that the rotational motion is transformed into reciprocating motion of the component with or without co-existing rotation, whereas, conversely, the forced reciprocating motion of one annular component relative to the other is transformed into rotational motion of the component with or without the coexistence of reciprocating motion.

009 The edges of the crests and valleys of the wavy surfaces of the two annular components may be points or straight sections perpendicular to the longitudinal axis, wherein if the edges of the crests and valleys are points, in the case of relative rotational motion between the two annular components in constant speed, generally simple and in special cases a harmonic reciprocity results, whereas if the edges of the crests and valleys are straight sections, in the case of relative rotational movement between the two annular components at constant speed, a reciprocity results with a delay in the reversal of movement in TDC and BDC proportional to the length of the straight sections. The reciprocating movement will be harmonic in the case of the flat propagation of these curves comprising sinusoidal curves without straight sections on the crests perpendicular to the longitudinal axis.

010 Note 1: In the previous paragraph, but also in the subsequent description as well as in the claims, whenever - for reasons of simplicity and brevity in expression - reference is made to "straight points or sections" of the top and valley edges and the “curves” of the wavy front surfaces of the annular components, in reality, this reference implies the flat propagation of the wavy curves of the external surfaces of the first, second and, whenever provided, third annular components from which the rays that form the adjacent corrugated (neighboring) surfaces of the annular components.

011 Note 2: In the description, as well as in the claims, whenever reference is made to contact "at at least one point" between the first and second or second and third annular components 1 and 2 or 2 and 3, respectively, this point intended to denote position. In fact, the contact is occurring in the straight sections of the spokes forming the wavy surfaces of the annular components 1, 2 and 3, which, under load, convert into narrow bands, that is, practically into narrow trapezoids.

012 The second annular component can function as a rotor and the first as a stator or vice versa. In the present description, applications are presented in which the second annular component functions as a rotor and the first as a stator.

013 An additional mechanism is provided, in many applications, forcing the second annular component to be pushed towards the first annular component so that the corrugated contact surfaces are in continuous contact with respect to each other.

014 Figures 1 to 20 show the operating principle of the mechanism and its applications. These drawings do not exactly follow the principles of mechanical engineering drawings. These illustrations were not drawn in great detail and include simplifications, the main ones being the following: a. Figures 5 to 13 do not show views, only semi-elevations: the arrangement with the rotor and the piston position in TDC appear on the right and left, the same in BDC. B. Certain components known to the person skilled in the art are shown as a single integral part, however, in reality they are complexes of more than one component. w. Usual engine parts known to those skilled in the art in the field (e.g. screws, ball bearings, bushings, gaskets, flanges, etc.) are not shown. d. Small axial lines indicate that neighboring components are firmly connected to each other.

015 Figures 1, 2, 3 and 4 show in a simplified way the principle of operation on which the present invention is based, while in Figure 2 (above) a simple set of valves is shown in a simplified way, controlling the flow of fluid, according to the present invention.

016 Figure 5 shows the cylinder of a piston engine having a movement transformation mechanism according to the invention, valves with openings, rotor cooperating with an axis through a spline, in addition to a reciprocating piston while it rotates.

017 Figure 6 shows the cylinder in Figure 5, the difference being that the stator is also a toothed belt that cooperates with the rotating axis.

018 Figure 7 shows the cylinder in Figure 5, the difference being that the shaft is connected to a toothed belt that cooperates with the rotating shaft.

019 Figure 8 shows the cylinder of an internal combustion piston engine having a movement transformation mechanism according to the invention, conventional valves, rotor cooperating with a shaft through a groove, disc-shaped control on the shaft plus a piston alternating as it rotates.

020 Figure 9 shows the cylinder in Figure 8, with the difference that the stator is also a toothed belt that cooperates with the rotating axis.

021 Figure 10 shows the cylinder in Figure 8, the difference being that the shaft is connected to a toothed belt that cooperates with the rotating shaft.

022 Figure 11 shows the cylinder in Figure 8, the difference being that the piston alternates without rotating.

023 Figure 12 shows the cylinder in figure 9, the difference being that the piston alternates without rotating.

024 Figure 13 shows the cylinder in figure 10, the difference being that the piston alternates without rotating.

025 Figure 14 shows a two-cylinder, double-acting symmetrical piston engine, with a movement transformation mechanism according to the invention, valves with openings or conventional, rotor cooperating with a shaft through a spline, in which the rotor is also a substitute for the piston, as the working fluid operates between the two stators, the rotor and a cylindrical body.

026 Figure 15 shows multi-cylinder arrangements based on Figures 5 to 14, in which absolute neutralization is achieved of the inertial forces resulting from the alternating masses of the rotor and piston.

027 Figure 16 shows clutch arrangements based on the motion transformation mechanism according to the invention.

028 Figure 17 shows differential arrangements based on the motion transformation mechanism according to the invention.

029 Figure 18 shows arrangements of the rotational speed increase-reduction/reciprocity reduction device based on the motion transformation mechanism according to the invention.

030 Figure 19 shows the coupling of an electric motor (power generator / electric motor) with two motors (motors or pumps / compressors, respectively) based on the movement transformation mechanism according to the invention.

031 Figure 20 shows engines based on the movement transformation mechanism according to the invention, with two mirror-symmetrical cylinders, a pair of corrugated surfaces per cylinder plus a mechanism that forces them into contact by pressure and with the aid of a spring.

032 In Figure 1, the motion transformation mechanism is shown, according to the invention, comprising a first annular component 1 and a second annular component 3 coaxially located, the first next to the second, along a longitudinal axis ΔA, the two components being capable of rotating around the longitudinal axis ΔA and reciprocating along the longitudinal axis ΔA. The side A of the first annular component 1 adjacent to the second annular component 3 is in continuous contact at at least one point with the neighboring side rα of the second annular component 3, so that the second annular component 3 can move relative to the first component annular element 1 being in continuous contact at at least one point with the neighboring side A of the first annular element 1. The contact sides are smooth wavy surfaces A, rα, shaped as a locus of the rays passing through the wavy curves α and yα, respectively, from the outer cylindrical surface of the first and second annular components 1, 3, starting from their outer surface and ending at their inner surface and being characterized by n (natural number ^ 0) repeating pairs of geometrically similar ridges and valleys with a similarity ratio 1:3, in which the crests/valleys are symmetrical with respect to the level defined by the upper/lower point of the crest/valley (respectively) and the longitudinal axis ΔA. In Figure 1 to 4, n = 2.

033 If the first annular component 1 and the second annular component 3 are forced into rotational motion relative to each other, while remaining in continuous contact, then each point of the wavy surfaces A, rα will trace, relative to the other, a wavy trajectory and will execute at the same time a reciprocating movement with a frequency n-times, where n is the number of crests/valleys, the corresponding rotational movement frequency, between a TDC (Top Dead Center) and a BDC (Bottom Dead Centre), this relative movement being performed by each component firmly connected to one of the annular components 1 or 3, on the other hand, each component connected to one of the annular components 1 or 3, so that this connected component is free not to follow the rotation of the component to which it is connected, performs reciprocating movement only, in relation to the other annular component, so that the rotational movement is transformed into reciprocating movement of the component with or without coexisting rotation, while, conversely, the reciprocating movement relative force of an annular component 1 or 3 with respect to the other is transformed into rotational movement of the component with or without the coexistence of alternative movement.

034 According to Figure 1, the crests of each and every wavy surface A, rα are smaller than the geometrically similar valleys with a similarity ratio of 1: 3, so that, when entering the valleys of the other, points of the crests in contact with points on the opposite corrugated surface, free space remains between the corrugated surfaces, resulting, when lubricated, in obtaining friction and minimizing wear due to dynamic lubrication.

035 In Figure 2, a movement transformation mechanism is shown, according to the invention, differing from the mechanism of Figure 1 in that it comprises an additional mechanism that forces the second annular component 3 to be pushed over the first annular component 1, to that the surface rα to be in continuous contact with the corrugated surface A. The additional mechanism comprises a third annular component 2, mounted coaxially with respect to the first and second annular components 1, 3 so that the second annular component 3 is located between the first and third annular components 1, 2, the adjacent side thereof, being the one facing the second annular component 3, is the wavy surface B characterized by the same wavy curve A as the first annular component 1, and by being its mirror image in space and in continuous contact at at least one point with its adjacent side of the second annular component 3, which is also the wavy surface rβ characterized by having the same wavy curve shape with the first annular component 1 of the adjacent side rα of the second annular component 3, but located symmetrical to the surface rα and displaced distally with the ridges located opposite the valleys of the surface rα, so that the second annular component 3 can rotate relative to the first and third annular components 1, 2 and in continuous contact in at least one point with one side of the first and with one side of the third annular component 1,2.

036 In the example of Figure 2, the second annular component 3 is connected to a piston 4 firmly or so that the second annular component 3 and the piston 4 are free to rotate independently around the longitudinal axis ΔA. Furthermore, a cylindrical body 5 is shown (disassembled in the extension of the longitudinal axis ΔA), within which moves - in circumferential contact - the cylindrical piston 4 covered by a cap 8. In this example, the second annular component 3 functions as a rotor, while the first and third annular components 1, 2 function as stators.

037 If the piston 4 is concave and firmly connected to the second annular component 3, and at least one opening 04 is located on the surface of the piston 4, in the case of rotational movement of the second annular component 3, the opening O4, tracing a wavy path And, meet at least one opening O5 of the fixed liner 5 found inside, or cross path E. The common points of the openings O4 and O5 allow periodic communication between the inside of the piston 4 and the outside of the liner 5, during the operating time. duration of the openings of the piston 4 and body 5 are communicating. Thus, a very simple arrangement of fluid flow control valves is created, between the internal space and the external environment, in a cylinder of a piston engine, through the concave piston 4 and body 5.

038 In Figure 3, spreads are shown of the wavy curves α, Yα/Yβ and β, respectively, of the outer cylindrical surfaces of the first, second and third annular components 1, 3 and 2 of Figure 2.

039 From Figures 3 it emerges that the crests of the corrugated surface of the first annular component 1 may be in contact with the crests of the corrugated surface of the second annular component 3 and that in this location the corrugated surfaces A, rα of the first annular component 1 and the second component annular 3 are in symmetry to a plane connecting their points of contact, whereas at this location the crests of the wavy surface B of the third annular component 2 are in contact with the troughs of the opposite wavy surface rβ of the second annular component 3 and the crests of the wavy surface of the second annular component 3 are in contact with the troughs of the opposite wavy surface of the third annular component 2.

040 From Figure 3, it emerges that, as long as the rotor 3 is rotated, each point of the rotor 3 and the piston 4, which is firmly connected to the rotor, will be moved tracing a closed wavy trajectory, with a spread similar to the ® curve, ( with equal crests and valleys that are geometrically similar to the crests and valleys of the wavy curves α, Yα/Yβ and β with similarity ratios 2:1 and 2:3, respectively), traced by point 3 of each crest of the rotor Yα curve 3. This movement, in the case of rotor 3 rotating with constant speed, is analyzed in a smooth circular movement with the same frequency and a reciprocal movement between TDC (Top Dead Center) and BDC (Bottom Dead Center) with double (generally n- times) frequency.

041 According to the invention, the edges of the crests and valleys are points or straight sections perpendicular to the longitudinal axis as represented in Figure 3, where if the edges of the crests and valleys are points, in the case of relative rotational movement of the rotor 3 between two annular components 1,3 with constant speed, a simple and/or harmonic reciprocity results, whereas if the edges of the crests and valleys are straight sections, in the case of relative rotational movement of the rotor 3 between two annular components 1, 3 with constant speed, a reciprocal movement results with an inversion delay at TDC and BDC.

042 In Figure 4, spreads are shown of the wavy curves α, Yα/Yβ and β, respectively, of the outer cylindrical surfaces of the first, second and third annular components 1, 3 and 2 of Figure 2, the only difference being that the third the annular component 3 is symmetric to the plane perpendicular to the longitudinal axis ΔA. In relation to Figure 3, the curves α and Yα are the same and in the same relative and absolute location as those in Figure 3, on the other hand the curves Yβ and β are the same and in the same relative location as those in Figure 3, in However, in a different position in relation to the curves α and Yα, resulting in the crests and valleys of the second annular element 3 being symmetrical and located on opposite crests and valleys, respectively. Also in this particular case, the second annular component 3 may be rotating relative to the first and third annular components 1, 2 by continuously contacting, at least at one point, one side of the first and one side of the third annular component 1, 2.

043 In Figures 3 and 4, for the curves α, Yα and, if there is the additional mechanism comprising the third annular component 2, for the curves β and Yβ the following applies: 1. It is approximately the same smooth, periodic and wavy at different locations with n (natural^0) number of repeating pairs of geometrically similar ridges 12345 and troughs 56789 with a similarity ratio of 1:3 (in Figures 1, 2, 3 and 4: n = 2). 2. The Yα curve is symmetrical to α in relation to the Ç-Ç axis. In Figure 3, the β curve results from the axial displacement (by d) of Yα, while Yβ by the axial (L + d) and circumferential displacement by 90o (generally 360o / 2n) of α. In Figure 4, the β curve results from the axial (L + d) and circumferential displacement by 90o (generally 360o / 2n) of Yα, while Yβ by the axial displacement (2L + d) of α. 3. Each ridge 12345 is symmetric about the μ-μ axis and each trough 56789 about the v-axis. The crests and valleys are expressed in the coordinate systems x1-y1 and x2-y2, with a common origin, point 5, and opposite axes, from the similar equations y1 = f (x1) and y2 = f (x2), respectively. The crests occupy 1/4 and the valleys the remaining 3/4 of the total height L of the wavy curves α, β, Yα and Yβ. 4. Sections 234 and 678 can be straight, where: 678>234>0 5. When the crests of one curve enter the valleys of the other, leave a free space between their curves, that is, the size of the crests is smaller than that of similar geometric valleys with a similarity ratio of 1:3. 6. If the outer surface of rotor 3 moves in one direction, while those of stators 2 and 3 remain motionless, it is proved that the curves Yα and Yβ will remain in continuous contact with the curves α and β, respectively, so that for point 3 (center of the crest) of the curve Yα, as well as for each spreading point on the outer surface of rotor 3, it is proven that it will move tracing a wavy trajectory like ®, (with equal crests and valleys that are geometrically similar to the crests and valleys of the wavy curves α, Yα/Yβ, and β with similarity ratios 2:1 and 2:3, respectively), with or without straight sections on their crests and valleys (Figures 3 or 4), as described below in section 9. The ® curve is expressed in the xy coordinate system, the point at the middle of the height L being the origin and at equal distance from the μ-μ and vv, from the equation y = f (x) which is similar to the equations y1 = f (x1) and y2 = f (x2). The total height of the curve ® is equal to the total height L of the wavy curves α, β, Yα and Yβ. 7. With reference to Figures 3 and 4, two characteristic pairs of equations are mentioned as an example, describing parts 45 and 56 of the α curve, respectively: a. (sinusoidal), where: B. (polonymic), where: The coordinates refer to suitably selected axes of coordinates for each equation, as mentioned above in section 3. 8. In the case of the curves of the previous section, the trajectory ® traced by each point of the propagation of the outer surface of the rotor 3 will be derived, respectively, from the equations: a. on what: (sinusoidal). B. twice, where: (polonymic). Coordinates refer to suitably selected coordinate axes for each equation as mentioned above in section 3. 9. If sections 234 and 678 are straight with a length (precisely) of c and 3c, respectively, between the curved sections of the trajectory or curvilinear motion ®, described by the previous equations of passage 8, equally interposed are equal sections of length 2c, corresponding to equal time intervals of delay in the inversion of motion in TDC and BDC. A different relationship (ratio) of the lengths of sections 234 and 678 presents problems, such as to bring about the insertion of unequal straight sections, i.e. a different motion reversal delay in TDC and BDC, possibly causing synchronization problems in multi-cylinder engines. Generally, equal delay time intervals in motion reversal in TDC and BDC result in the case where the ridge edges are straight sections of length c and the valley edges are straight sections of length 3c, respectively.

044 Note: In order to achieve a - desirable - smooth periodic wavy trajectory or curvilinear motion ® (from all points on the outer surface of rotor 3) with equal crests and valleys, we specify the wavy curves α, Yα/Yβ and β, of so that the crests and valleys are similar to the crests/valleys of the ® curve with a similarity ratio of 1:2 and 3:2, respectively. Then, rotor 3 rotates and moves back smoothly, sliding - continuously contacting - stators 1 and 2 simultaneously, however, this is not true if the crests of the curve ® are not equal to its valleys, because the movement of stator 3 is blocked.

045 Definition: We say that a geometric shape ∑2 is similar to some other geometric shape ∑1 (with respect to a common coordinate system), as long as the coordinates of ∑2 result from the corresponding coordinates of ∑1 by multiplying them by similarity ratio. The similarity ratio can be greater than, less than, or equal to one; therefore, we can obtain enlargement, reduction or equality for ∑1 respectively.

046 Figures 5, 6 and 7 show applications in piston engines (motors or pumps / compressors) having an integrated motion transformation mechanism, according to the invention, comprising an additional mechanism with a third annular component 2 and a matrix of valve according to the invention. Said engines comprise one or more cylinders (in parallel and/or opposite arrangement for the neutralization of inertial forces), wherein the second annular component 3, functioning as a rotor, is firmly connected to a cylindrical piston 4 rotating and reciprocating simultaneously. Said engines comprise auxiliary systems (lubrication, cooling, fuel, starting, etc.) known in the art.

047 The first and third annular components 1, 2 operate as stators and are firmly mounted in a body 7, while the rotor 3 is rotating and alternating axially in accordance with the invention, moving through a spline of a shaft 6 coinciding with the axis of the piston engine cylinder in Figure 5, or the axis 6 moving through the axis 11 located outside the cylinder, parallel to its axis, as appears from Figure 7, in which the movement is transmitted to the axis through a shaft 11 via gears 12 and 15. In Figure 6, the movement is transmitted to the rotor by a shaft 11 through gear 12 and rack on the outer surface of the rotor 3. The length of the gear 12 allows continuous engagement of the same to rotor 3 as it alternates during rotation. Indicator 16 shows a body cover 7.

048 In Figures 5, 6 and 7, the cylinder is supplemented by a cylindrical casing 5, within which moves - in circumferential contact - the piston 4 covered by a cylinder cover 8. Also included are the piston rings 9 and the valve spring 10.

049 In each valve with openings (one opening in the body and another in the piston) of the type of the present invention, one opening is circular and the other, when the fluid is decompressed. Furthermore, in applications where there are hydraulic piston motors or pumps/compressors and 2-stroke ICEs, the number of valve openings (both suction and compression) of the type of the present invention is twice the number n of crests/ valleys, while the number of valves of 4-stroke ICEs is equal to n.

050 In Figures 8, 9 and 10 applications are shown in piston engines (motors or pumps / compressors) with an integrated motion transformation mechanism according to the invention, including additional mechanism with a third annular component 2, in which the second annular component 3 functions as a rotor is firmly connected to the piston 4 rotating and alternating simultaneously in combination with conventional/classical valves 18. Said engines are constituted by one or more cylinders (in parallel and/or opposite arrangement, for the neutralization of inertial forces) with a common axis 11 and state-of-the-art auxiliary systems (lubrication, cooling, fuel, starting, etc.).

051 Figure 8 differs from Figure 5 in that the valve arrangement according to the invention has been replaced by conventional / classical valves 18. A disc-shaped cam 13 can be distinguished fitted directly above the shaft 6 plus the rods 17 required in the case of an ICE.

052 Figure 9 differs from Figure 6 in that the valve arrangement according to the invention has been replaced by conventional / classical valves 18. A disc-shaped cam 13 can be distinguished fitted directly above the shaft 11 plus the rods 17 required in the case of an ICE.

053 Figure 10 differs from Figure 7 in that the valve arrangement according to the invention has been replaced by conventional / classical valves 18, while in the case of an ICE a disc-shaped cam 13 fitted directly above the shaft 11 and rods 17 They are provided.

054 Figures 11, 12 and 13 differ from Figures 8, 9 and 10, respectively, in that the piston 4 is connected in such a way to the rotor 3 so as to be free to not follow the rotation of the rotor 3, causing the rotation of the axis 6 or axis 11, and to perform only reciprocating movement within the body 5. This is achieved through linearly sliding elements 14 (wedges, spheres, etc.).

055 Since the piston performs reciprocating movement only within the body 5, the described mechanism can be combined only with conventional / classical valves 18 and, in the case of (ICEs), with a disc-shaped cam 13 mounted directly above the shaft 6 or 11 shaft, plus 17 rods.

056 In Figure 14, another application of a double-effect piston engine (motor or pump/compressor) according to the present invention, in which the working fluid operates between the stators 1 and 2, the rotor 3 and a cylindrical body 5/7. Specifically, a double-acting two-cylinder piston engine is shown, with a motion transformation mechanism, open or conventional valves, rotor 3, rotation on axis 6 with a sliding groove, in which the role of the piston is performed by the rotor 3, since the working fluid operates between the two stators 1 and 2, rotor 3 and cylindrical body 5/7.

057 As in Figures 5 to 13, the engine can operate, with simple openings like valves according to the invention in the stator 3 and in the body 5/7, but also with various types of conventional/classical valves above the body 5/7.

058 In order to neutralize inertial forces, the indication is to combine, as in Figure 14, two opposing stators 3 with the corresponding stators 1 and 2 in the same body 5/7, or to suitably combine more cylinders, as in Figure 15. In this application , the cases of 2-stroke ICEs, hydraulic motors and pumps/compressors are of particular interest.

059 The motors presented in Figures 5 to 14 perform in each of their rotations as many reciprocations as the number n of crests/valleys existing on each wavy surface of stators 1, 2 and rotor 3. The case in which n = 1 is infrequent due to a the emergence of asymmetric internal forces causing friction forces between the piston 4 and the body 5 and relative wear. Typically n = 2, thus, in 4-stroke ICEs incorporating the present invention, each cycle of operation is completed in one revolution versus two revolutions in conventional ICEs. This results in (approximately) doubling the power for the same displacement engines. The effect is opposite - in combination with the absence of the piston rod and classic camshaft - on the engine size/weight: it is reduced (approximately) by 50% for the same power. The above items apply and are generalized according to n> 2.

060 The same also applies to 2-stroke ICEs where once again the power is doubled or the size/weight is halved compared to conventional 2-stroke engines for the same displacement or power respectively.

061 Finally, in all ICEs incorporating the present invention and using a disc-shaped control, absolute control is made possible of the stroke, time and duration of activation of conventional / classical valves, due to the fact that there are no restrictions in the choice the position and configuration of the shape and size of the controls.

062 In Figure 15, the arrangements are shown based on the applications corresponding to Figures 5 to 14, in which absolute neutralization is achieved of the inertial forces resulting from the alternating masses of the rotor 3 and the piston 4 without equilibrium: the arrows show the relative movement in the various cylinders. Whenever possible, combustion is carried out consecutively in the various cylinders and shared equally in each rotation of shaft 11, for reasons of smoothing the power flow.

063 Specifically, in figure 15, the following interesting cases are presented: a. 2 cylinders placed in opposite arrangement, with working fluid chambers at the ends, and with a power output from a parallel shaft with two output positions. The specific arrangement constitutes a simple autonomous operating unit (SUAO) with the reciprocal inertial forces completely balanced. B. 2 cylinders placed in opposite arrangement, with the working fluid chambers unified or not in the center, and with a power output from a parallel axis with two output positions. In ICEs, the unified chamber casing is at a disadvantage compared to the separate chamber casing due to half the speech location of the combustions, resulting in greater fluctuations in the energy flow curve. This arrangement constitutes another version of a simple autonomous operating unit (SUAO). w. 4-cylinder or multi-cylinder engine composed of case 15.a units for smoother operation and/or greater power with a single output. d. 4-cylinder or multi-cylinder engine composed of the units in Figure 15.b for smoother operation and/or greater power with a single output. It is. 4 cylinders arranged in parallel on the same level, with two power outputs that constitute the extension of the axles 6. f. 4 cylinders arranged in parallel on the same level, with a parallel power outlet in the center with two ends. g. 4 cylinders arranged in parallel and in a circle (every 90o), with a parallel power outlet in the center with two ends. H. 4 cylinders arranged in parallel and in a circle (cross), with a parallel power outlet in the center with two ends.

064 Additionally, for the applications of Figures 5 through 14, the following observations are in effect: 1. The working fluid operates within the body 5, between the free surface of the piston 4 and the cap 8. 2. In Figures 5, 7, 8, 10, 11, 13 and 14, axis 6 coincides with the cylinder axis. 3. In Figures 6, 9 and 12, axis 11 is positioned outside the cylinder, parallel to its axis. Movement from shaft 11 to rotor 3 is transmitted through gear 12 and rack on the outer surface of rotor 3. The reverse also applies. The length of the rack 12 allows continuous engagement of the rotor rack 3 as it alternates during rotation. 4. In Figures 8 and 11, where conventional valves 18 are used, the disc-shaped control 13 is positioned on shaft 6. 5. In Figures 9, 10, 12 and 13, where conventional valves 18 are also used used, the disk-shaped command 13 is positioned on the axis 11 and on its disk it supports only one set of commands. These cases are recommended for multi-cylinder engines, provided that the cylinders are arranged in parallel and at an equal distance (circularly) around the single axis 11 (see Figures 15 g and 15h). 6. In Figures 7, 10 and 13, shaft 11 is driven by shaft 6 through a pair of gears 12 and 15. Reverse also applies. 7. In Figures 8 to 13, when referring to applications in hydraulic piston motors or pumps/compressors, conventional/classic valves suitable according to the specific configuration are used. Valves, piston rods and the crankshaft disc (referring to ICEs) are abolished. 8. In Figures 5, 6, 7 and 14, when reference is made to applications in engines or hydraulic piston pumps, in each pair of valves with openings (type of the present invention) one is circular and the other oblong, when the fluid is uncompressed. 9. In Figures 5, 6, 7 and 14, when reference is made to applications in piston hydraulic motors or pumps/compressors and 2-stroke ICEs, the number of valve openings (type of the present invention) is twice the number ° of valves in 4-stroke ICEs. 10. In Figures 5, 7, 8, 10, 11, 13 and 14, the rotation and simultaneous reciprocating movement of the rotor 3 are achieved with a groove above the axis 6, while in Figures 6, 9 and 12 via a toothed belt 12 and external rack on rotor 3.

065 In the cases described through the illustrations in Figures 5 to 14, the transformation from rotational movement to reciprocating movement and vice versa is carried out due to the sliding of the surfaces rα and rβ of the second annular component 3, which can also function as a rotor , on the surfaces A and B, respectively, of the first and third annular components 1 and 3, which can function as stators, as shown in Figures 2, 3 and 4. The same result also arises in the case that the surfaces rβ and B are eliminated and the second annular component 3 is forced to be pushed towards the first annular component 1, so that the surface rα is in continuous contact with A. This can be achieved, for example in the following ways, by replacing the third annular component 2: 1. Use spring(s) exerting pressure on rotor 3, in combination with bearings, except in special cases (as in the case of Figure 20). 2. With two diametrically opposed rollers, mounted on rotor 3, rolling over a suitable corrugated surface formed on stator 2, similar to surface B (Figure 2), so that the roller axes trace the curve ® of Figure 3 or 4. 3. Using pressure (hydraulic or pneumatic) on rotor 3. 4. Using a magnetic/electromagnetic force arrangement on rotor 3. 5. Using the force of gravity (only for engines with vertical cylinders).

066 Finally, the present invention applies to all types of motors and automations in which the transformation from rotational movement to reciprocal or the reverse is occurring, such as in mechanical presses, nail making machines, sewing machines, printing machines, etc. .

067 In Figure 16.a, the arrangement of a clutch is shown comprising a first annular component 1 connected to the shaft 6 with an axially sliding spline, a component (secondary shaft) 4 firmly connected to the second annular component 3, at the same time a component special mechanism, according to the state of the art, can exert an axial force F on the first annular component 1 and forces its crests to enter the valleys of the second annular component 3. In this condition, the rotation of the axis 6 is transferred completely to the secondary axis 4. If the axial force F on the first annular component 1 is high, it will move back and detach from the second annular component 3, in which case the transfer of rotation from axis 6 to secondary axis 4 will be interrupted.

068 In Figure 16.b a more effective clutch arrangement is shown, in which the shaft 6 is connected via a sliding spline to the rotor 3, that is, with the second annular component, the stator 2, that is, the third annular component, is firmly connected to component (secondary shaft) 4, on the other hand, in this position/initial condition the rotor 3 slides simultaneously and moves freely between stators 1 and 2, without affecting its kinematic condition. Furthermore, a special mechanism, according to the state of the art, can exert an axial force F on the stator 1, forcing the first and third annular components 1 and 2 to come sufficiently close to each other. In this new condition, rotor 3 is immobilized between stators 1 and 2; Therefore, the rotation of shaft 6 is transferred in full effect to secondary shaft 4. If the axial force F on stator 1 is lifted, by the special mechanism it will move back to its initial position/condition, rotor 3 will be released and start moving sliding between stators 1 and 2 again, and the transfer of rotation from axis 6 to secondary axis 4 will be interrupted.

069 Optionally, stators 1 and 2 are externally connected to a casing 7: the first with axially sliding wedges 14 and the third enabled to rotate only slightly.

070 The special mechanism that exerts force F enjoys wide application in the current state of the art, may be somewhat equivalent to the mechanisms found in the clutches of all types of vehicles (cars, trucks, tractors, etc.) and may function mechanically and/or hydraulically and/or pneumatically etc.

071 A feature/advantage of such a clutch is the simple and compact construction, but mainly, the transfer of movement with mechanical engagement, not friction, resulting in the (almost complete) lack of wear, due to the absence of friction during the sliding action of the clutches. cooperating parts, due to their hydrodynamic lubrication.

072 In Figure 17.a, an arrangement for a differential is shown, comprising two symmetric mirror image sections, each consisting of a first annular component 1 and a second annular component 3 connected to a shaft 6 with a sliding spline. A special mechanism, in accordance with the state of the art, exerts force F on the first annular component 1 and keeps it engaged with the second annular component 3. Each of the two annular components 3 is firmly connected to a toothed belt 15 that moves through of the shaft 11 by means of the cooperating toothed belt 12. As long as the resistance of two of the moving shafts 6 is the same, the first annular components 1 remain engaged with the second annular components 3 and the rotation of the toothed belt 15 is transferred to their effect total for axes 6. If the resistance increases in one of the axes 6, the first corresponding annular component 1 will move back and the no. of rotations of the corresponding axis 6 will be decreased, at the same time the other axis 6 will continue moving normally until the balance in the resistances of its axis 6 returns, and the previous operation is restored. In other words, the arrangement works as a simple differential. To avoid the disadvantage of the immobilization of one axis 6 and the rotation of only the other, if the resistance of the latter is zero, it is essential that the control of the forces F and the rotations of the axes 6 is carried out by means of electronic assistance. In this case, both axles can be blocked completely and both axles can be rotating at the same speed: "LSD" limited slip differential.

073 In Figure 17.b, a more effective differential arrangement is provided as a combination of the arrangements shown in Figures 16.b and 17.a, the combined descriptions of which provide the mode of operation of this particular type of differential. The differential arrangement comprises two symmetrical mirror image sections, each consisting of the second annular component 3, functioning as a rotor, connected to a shaft 6 via a sliding spline, a first annular component 1 and a third annular component 2. In this initial position/condition, rotor 3 slides, and at the same time moves freely, between stators 1 and 2 without affecting its kinematic condition. A special mechanism, according to the state of the art, exerts a force F on the first annular component 1 moving towards the third annular component 2, trapping and immobilizing the second annular component 3 between the first and third components 1 and 2, so that the third annular component 2 is firmly engaged and moving simultaneously with the axis 6. The two symmetrical mirror image sections are firmly connected by means of third annular components 2 to a toothed belt 15, moving from an axis 11 by means of a cooperating toothed belt 12. The operation of the arrangement as a differential is determined by whether or not the second annular component 3 is trapped and immobilized. Thus, as long as the resistance of two axes 6 during movement is the same, the second annular components 3 remain engaged with the third ring components 2 and the rotation of the timing belt 15 are carried in their full effect to the axes 6, on the other hand, if the resistance increases in one of the axes 6, the corresponding first annular air component 1 will retreat slightly, the second corresponding annular component 3 will be released and will start to slide simultaneously and move freely between the first and third annular components 1 and 2, hence the no. of rotations of the corresponding shaft 6 will decrease until the balance of the resistances of the shafts 6 is restored and the arrangement returns to its initial operating position/condition.

074 Optionally, the first annular component 1 is connected to a body 7 through the use of axial sliding 14, and the third annular component 2 is connected to the body 7 having the capacity for slight circumferential sliding.

075 The special force exerting mechanism F, as in the differential arrangement applications of Figures 16.a and 16.b, can operate mechanically and/or hydraulically, and/or pneumatically etc., with or without electronic assistance.

076 A feature/advantage of such a differential is the simple and compact construction, but mainly, the transfer of motion via mechanical engagement, not friction, resulting in the (almost complete) lack of wear, due to the absence of friction during the sliding action of the cooperating parts, due to their hydrodynamic lubrication, as well as the ability to operate as an “LSD” differential.

077 In Figure 18.a, a first mechanism for transforming rotational motion into reciprocal motion or vice versa is shown, in accordance with the present invention, with n = n1 number of crests and valleys, in which a first and a third annular component 1 and 2 function as stators and are firmly mounted in a body 7, while the second annular component 3 is moved by a shaft 6 with a sliding spline and functions as a rotor firmly connected to a piston 4 rotating and reciprocating axially, coaxially connected via a pin 19 to a second similar mechanism, with the same reciprocity path L and a number of crests and valleys n = n2 + ni, via pistons 4 so as to allow rotation relative to each other, however, not axial displacement. In this case, if axis 6 of the first mechanism rotates with N1 rotations, then axis 6 of the second mechanism will be rotating with rotations N2 = N1 x (n1 / n2), that is, the pair of mechanisms works as an increase in speed. rotation - reduction device.

078 In Figure 18.b, respectively, the axes 6 of the two mechanisms are coaxially connected by means of wedges 14 of a coupler 20 in a fixed way, therefore, the pair of mechanisms functions as an alternative device for reducing the increase in speed. In the latter case, it can also function and/or as an alternative path length increase-reduction device L, provided that the alternative path length L1 of the first mechanism is different from the alternative path length L2 of the second.

079 A feature/advantage of such a step-down device is the in-line (coaxial) arrangement and capacity in addition to increasing/reducing the no. of rotations, to achieve increasing/reducing the number of reciprocations as well, with or without changing the path length.

080 Figure 19 shows the coupling of an electric motor (power generator / electric motor) with two similar M motors (motors or pumps / compressors, respectively) as those described in the applications reported in Figures 5, 8 and 11 of the present invention. The motor bodies M are mounted coaxially on the body (stator) of the electric motor E: one on the right and one on the left. The rotor shaft of the electric motor E is abolished and is replaced by the 6 shafts of the motors M, and with this they synchronize with each other, resulting in operation with pistons moving in opposite directions so that the inertial forces of reciprocity to balance. This type of coupling corresponds to Figure 15.a, but offers an advantage over it, as the parallel shaft is absent, having been replaced by the electric motor rotor.

081 A feature/advantage of such an electromechanical pair is its simplicity, the particularly small size/weight, the high energy concentration and the compactness (compact) of the construction compared to other conventional cases.

082 In Figures 5 to 14, the described engines of the present invention can operate as 2-stroke gasoline engines with clean fuel (without adding lubricant). Fuel injection with spraying is required, air intake using a compressor (turbo), a construction that allows delay of the reversal of motion at TDC and BDC according to the present invention and valves with openings according to the present invention, or controlled by a disc in the form of a command, and regulated (a possibility also provided by the present invention) to operate in the following order: as soon as the expansion phase is completed and just before the piston reaches BDC, the outlet valve opens and the Most of the gases escape then the inlet valve opens and the incoming air under pressure forces the remainder of the exhaust gases out (sweep/wash), the outlet valve closes followed by the inlet valve once the cylinder is filled with air and the reversal of motion begins towards TDC. Then comes the phase of compression, injection, ignition and combustion of the fuel and, finally, expansion, and a new identical cycle begins again.

083 A feature/advantage of such a 2-stroke gasoline engine is its small size/weight, about half that of a conventional 2-stroke gasoline engine with the same power, plus its non-polluting operation, i.e. the emission of exhaust gases comparable in quality to 4-stroke gasoline engines, unlike the polluting exhaust gases of conventional 2-stroke gasoline engines.

084 The described engine can also operate in the same way as a diesel engine.

085 In both cases (gasoline or diesel engine), its size/weight is about a quarter of the size/weight of the corresponding conventional 4-stroke engine.

086 Figure 20 shows the application of a mechanism in a two-cylinder piston engine, corresponding to that in Figure 15.a, in which the cylinders are coaxial, mounted in a mirror image arrangement, with two components 4 moving in opposite directions - functioning as pistons - to balance the inertial forces of reciprocity and characterized by each cylinder operating with a pair of annular components with wavy surfaces that transform the movement on their adjacent sides, in accordance with the present invention, and their contact continuous ensures a force is continually exerted on the piston as it moves from TDC to BDC and vice versa.

087 More specifically, in Figure 20, each cylinder comprises a first annular component 1 functioning as a stator, a second annular component 3 functioning as a rotor firmly connected to a piston 4. The stators 1 are firmly connected to each other and to a common body 7. Each rotor 3 carries an external rack cooperating with a toothed belt 12 mounted on a common axis 11, parallel to the longitudinal axis of the cylinders. Gears 12 synchronize rotors 3 and transfer motion to shaft 11. A force is exerted on pistons 4 as they move between TDC and BDC, which is due to working fluid pressure and/or assist of a traction spring 21, keeping the corrugated surfaces of the rotors 3 in contact with the respective stators 1. The traction spring 21 connects the pistons (4) to each other through openings in the stators 1, therefore it acts to assist their recovery, keeping the rotors 3 in continuous contact with the respective stators 1, a fact that is particularly important during the period in which the engine is not running, thus avoiding its detuning. Each cylinder comprises valves according to the invention or conventional/classic valves 18, in combination with disc-shaped controls 13 and rods 17. These engines are the 2-stroke ICEs, the hydraulic and air engines, in which the force on the piston is due to the pressure of the working fluid. Pumps/compressors constitute a similar case, in which the force on the piston in the suction phase is exerted exclusively by the tension spring 21; in relation to other elements, the same applies as established in the case of engines.

088 A feature/advantage of such an engine is its simplicity, the particularly small size/weight, the high power concentration and the compactness of the construction compared to other conventional enclosures.

089 The advantages of the mechanisms of the present invention, compared to the disadvantages of existing ones, as well as the advantages of their implementation in piston engines (motors or pumps/compressors) and in automation are the following: 1. The exceptionally simple and the very small number of components required for its implementation. 2. The minimum number of moving components: only shaft 11 or shaft 6, rotor 3 and piston 4. 3. The possibility of implementing the valve arrangement with simple openings, without additional components and / or mechanisms. 4. The possibility of combining with conventional valves 18 and controls (ICE) in a disc-shaped control 13 on shaft 6 or shaft 11. The controls can be molded into suitable configurations so that they can open and close the valves in a more effective at predetermined times. 5. The possibility of achieving absolutely harmonious reciprocity without higher order harmonics. 6. The reciprocating movement of piston 4 can be carried out in several ways and described by simple mathematical equations. Typical cases of equations are sinusoidal and polyonymic. 7. The possibility of delaying the inversion of piston movement at TDC and BDC for better combustion and greater efficiency. 8. The possibility of completely neutralizing the inertia forces of the reciprocating movement without balancing, only with the appropriate arrangement of the cylinders. 9. The substantial absence of friction and wear between piston 4 and body 5 due to the total lack of transverse forces between them. 10. The sub-multiple force (half being the maximum, for n = 2), exerted at the contact points of the corrugated sliding surfaces A, B and rα/rβ of stators 1, 2 and rotor 3, relative to the force exerted at the pin-piston rod contact point of a conventional engine. 11. The minimization of friction and wear of the corrugated sliding surfaces A, B and rα / rβ of stators 1, 2 and rotor 3 respectively, due to the dynamic lubrication developed due to the favorable geometry. 12. The manufacturing capacity of 2-stroke ICEs with anti-pollution technology of size/weight/cost is approximately 50% of conventional 2-stroke ICEs or 25% of conventional 4-stroke ICEs. 13. The compact construction of multi-cylinder engines: it is possible to arrange the cylinders in line with one (Figure 15.f) or two opposing axes (Figure 15.e), or transversely and transversely with a central axis (Figures 15.g and h, respectively ). 14. The reduction of approximately 50% in size and/or volume for the same power and, consequently, the doubling of the power concentration. The reverse also applies. 15. Approximately 50% reduction in cost due to corresponding reduction in size and/or volume for the same power. Figure Index: 1. First annular component, stator. 2. Third annular component, stator. 3. Second annular component, rotor. 4. Piston or secondary clutch shaft. 5. Body. 6. Shaft with sliding groove. 7. Body. 8. Cylinder cover. 9. Piston rings. 10. Valve spring (opening). 11. Axis (common). 12. Shaft timing belt. 13. Disc-shaped controller. 14. Sliding element (wedge). 15. Shaft timing belt. 16. Body coverage. 17. Valve stem. 18. Conventional / classic valve. 19. Coupling pin. 20. Coupler. 21. Traction spring.

Claims (16)

1. MECHANISM FOR TRANSFORMING RECIPROCAL MOTION INTO ROTATIONAL OR VICE-VERSA AND APPLICATIONS THEREOF is characterized by comprising a first annular component (1) and a second annular component (3) located coaxially, the first next to the second, along a longitudinal axis (ΔA), in which both annular components are capable of rotating about the longitudinal axis and reciprocating along the longitudinal axis, the first (1) and second (3) annular components each have a corrugated surface ; wherein, a side (A) of the first annular component (1) adjacent to the second annular component (3) is in continuous contact, at at least one point, with the opposite side (rα) of the second annular component (3), such that the second annular component (3) is capable of moving coaxially with respect to the first annular component (1) in continuous contact at at least one point with the adjacent side (A) of the first annular component (1), wherein the surfaces The wavy sides of the contact sides are smooth wavy surfaces (A, rα) formed as a locus of rays passing through smooth wavy curves (α, Yα), respectively, of the outer cylindrical surface of the first and second annular components (1, 3), starting from its outer surface and characterized by n (natural number^0) repeating pairs of geometrically similar ridges and valleys with a similarity ratio 1:3, the similarity ratio being defined as the ratio of the coordinates of two geometric shapes similar with respect to a common coordinate system wherein a first geometric shape is similar to a second geometric shape with respect to a common coordinate system, provided that the coordinates of the first geometric shape result from the corresponding coordinates of the second geometric shape by multiplying them by the similarity ratio, in which the crests/valleys are symmetrical with respect to the level defined by the highest/lowest point of the crest/valley (respectively) and the longitudinal axis, in which the crests of the wavy surface of the first annular component (1 ) may be in contact with the crests of the corrugated surface of the second annular component (3) and in which in this position the contact points are located in a plane perpendicular to the longitudinal axis, relative to which the corrugated surfaces (A, rα) of the The first annular component (1) and the second annular component (3) are symmetric, in that the crests of each wavy surface (A, rα) are smaller than the geometrically similar valleys with a similarity ratio of 1:3, so that, when they enter the valleys of each other, and the edges of the crest come into contact with the lowest point of the opposite corrugated surface, free space remains between the corrugated surfaces, resulting, when lubricated, in friction and minimized wear due to dynamic lubrication; so that, if the first annular component (1) and the second annular component (3) are forced into rotational movement with respect to each other, remaining at the same time in continuous contact, all points of the corrugated surfaces (A, rα ) will trace, in relation to the other, a wavy trajectory and, at the same time, execute, in relation to the other, an alternative movement with a frequency of “n” times, where “n” is the number of crests / valleys; the frequency of corresponding rotational movement, between a TDC (Top Dead Centre) and a BDC (Bottom Dead Centre), this relative movement being executed by each component firmly connected to one of the annular components (1, 3), while each component connected to one of the annular components (1, 3), so that this connected component is free not to follow the rotation of the component to which it is connected, perform only reciprocating movement, in relation to the other annular component, so that the rotational movement is transformed into reciprocating motion of the component with or without coexisting rotation, while, conversely, the forced relative reciprocating motion of one annular component (1, 3) with respect to the other is transformed into rotational motion of the component with or without coexisting reciprocating motion, wherein the edges of the crests and valleys in a plane spread of the wavy curves of the outer surfaces of the first and second annular components are points or straight sections vertical to the longitudinal axis, wherein if the edges of the crests and valleys are points, in the case of motion relative rotational between the two annular components (1,3), constant speed results in a simple and/or harmonic reciprocity; on the other hand, if the edges of the crests and valleys are straight sections, in the case of rotational movement between the two annular elements (1,3) with constant speed, a reciprocity results in a delay in the reversal of movement in TDC and BDC , where the edges of the ridges are straight sections of length “c”, and the edges of the valleys are straight sections of length “3c”, respectively, with the result being time intervals with equal delays in inverting motion at TDC and BDC. 2. MECHANISM FOR TRANSFORMING RECIPROCAL MOTION INTO ROTATIONAL OR VICE VERSA AND APPLICATIONS THEREOF is characterized in that, according to claim 1, the second annular component (3) is connected to a cylindrical component (4) firmly or in such a way that the second annular component (3) and the cylindrical component (4) have the freedom of at least one to remain stationary, alternate along the longitudinal axis and rotate around the longitudinal axis independently of each other. 3. MECHANISM FOR TRANSFORMING RECIPROCAL MOVEMENT INTO ROTATIONAL OR VICE-VERSA AND APPLICATIONS THEREOF is characterized by, according to claim 2, a cylindrical coating (5), within which it moves in circumferential contact with respect to the cylindrical piston ( 4) covered by a cover (8), the cylindrical piston being the cylindrical component. 4. MECHANISM FOR TRANSFORMING RECIPROCAL MOTION INTO ROTATIONAL OR VICE VERSA AND APPLICATIONS THEREOF is characterized in that, according to claim 3, the cylindrical piston is a hollow piston (4) and is firmly connected to the second annular component (3) and on the surface of the piston (4) there is at least one opening (O4) which, when tracing a wavy path (E), meets at least one opening (O5) in the coating (5) located inside or on the transverse path (E), allowing periodic communication between the inside of the piston (4) and the outside of the casing (5), since the piston (4) and casing (5) openings share common points, creating a very simple valve arrangement that controls the fluid flow between the internal space of a piston engine cylinder and external environment, through the hollow piston (4) and casing (5). 5. MECHANISM FOR TRANSFORMING RECIPROCAL MOVEMENT INTO ROTATIONAL OR VICE VERSA AND APPLICATIONS THEREOF is characterized in that, according to claim 1, 2, 3 or 4, it comprises an additional mechanism that forces the second annular component (3) to be pushed to the first annular component (1), so that the corrugated surface (rα) of the second annular component (3) is in continuous contact with the corrugated surface (A) of the first annular component (1). 6. MECHANISM FOR TRANSFORMING RECIPROCAL MOTION INTO ROTATIONAL OR VICE VERSA AND APPLICATIONS THEREOF is characterized in that, according to claim 5, the additional mechanism comprises a third annular component (2), mounted coaxially with respect to the first and second components annular components (1,3), that the second annular component (3) is located between the first and third annular components (1,2), the corrugated surface (rα) of the second annular component (3) is a first corrugated surface ( rα) and the second annular component (3) also has a second wavy surface (rβ), an adjacent side of the third annular component (2), being the one towards the second annular component (3), is a wavy surface (B) , wherein a corrugated surface (B) of the third annular component (2) is comprised by the same corrugated surface (A) of the first annular component (1) and is in continuous contact at at least one point with a side of the second annular component (3) adjacent thereto, which is also the second corrugated surface (rβ) of the second annular component (3), wherein the second corrugated surface (rβ) of the second annular component (3) is understood to have the same corrugated surface as the side (rα) of the second annular component (3) being adjacent to the first annular component (1), wherein, the first and second corrugated surfaces (rα, rβ) of the second annular component (3) are disposed relative to each other another such that: crests of the second corrugated surface (rβ) are axially aligned with valleys of the first corrugated surface (rα), and the corrugated surface (B) of the third annular component (2) is a mirror image of the corrugated surface (A ) of the first annular component (1), or valleys of the second corrugated surface (rβ) are axially aligned with the valleys of the first corrugated surface (rα), such that the first and second corrugated surfaces (rα, rβ) of the second annular component (3) are in mirror symmetry with each other and the valleys of the corrugated surface (B) of the third annular component (2) are axially aligned with crests of the corrugated surface (A) of the first annular component (1), the second annular component (3) can move relative to the first and third annular components (1, 2) and in continuous contact at at least one point with one side of the first annular component (1), and with one side of the third component annular (1, 2), in which the crests of the corrugated surface (A) of the first annular component (1) can be in contact with the crests of the corrugated surface (rα) of the second annular component (3) and that in this location the surfaces wavy surfaces (A, rα) of the first annular component (1) and the first wavy surface (rα) of the second annular component (3) are both in symmetry with a plane connecting their points of contact, while at this location the surface crests wavy surface (B) of the third annular component (2) is in contact with the troughs of the second wavy surface (rβ) of the second annular component (3) and the crests of the wavy surface of the second annular component (3) are in contact with the troughs of the wavy surface of the third annular component (2), as a result of the geometrically similar crests and valleys with the similarity ratio 1:3. 7. MECHANISM FOR TRANSFORMING RECIPROCAL MOTION INTO ROTATIONAL OR VICE VERSA AND APPLICATIONS THEREOF is characterized by, the application of the mechanism, according to claim 6, a piston engine cylinder, in which the first and third annular components ( 1, 2) operate as stators and are firmly mounted in a body (7), while the second annular component (3) functions as a rotor, firmly connected to the piston (4) rotating and alternating axially, or connected with the possibility of rotating with the piston (4) reciprocating only axially, moving through a groove of a shaft (6) coinciding with the axis of the piston engine cylinder or moving from the shaft (6) through the shaft (11) mounted outside the cylinder, parallel to its axis, wherein the movement is transmitted to the shaft (6) from the shaft (11) by means of gear wheels (12, 15) or moving by an shaft (11) through the timing belt (12) and rack on the outer surface of the rotor (3), wherein valves with openings are provided according to claim 4, or conventional/classic valves (18) and, in the case of ICEs, conventional/classic valves (18) in combination with disc-shaped camera (13) and rods (17). 8. MECHANISM FOR TRANSFORMING RECIPROCAL MOTION INTO ROTATIONAL OR VICE VERSA AND APPLICATIONS THEREOF is characterized by, the application of the mechanism, according to claim 7, a piston engine cylinder, in which the engine operates as a gasoline engine 2-stroke with clean fuel without adding lubricant, in which fuel injection is required, air intake with forced induction with equal time intervals of delay in inverting movement at TDC and BDC, according to claim 1, and valves with openings according to claim 4, or controlled by a disc-shaped camera (13) and rods (17), wherein the valves operate in the following order: as soon as the expansion phase is completed and just before the piston reaches the BDC, the outlet valve opens and most of the exhaust gases escape, then the inlet valve opens and the incoming air under pressure forces out the rest of the exhaust gases (sweep/wash), the outlet valve is closed followed by the inlet valve when the cylinder is filled with air and the reversal of movement begins towards TDC, followed by the compression phase, ignition and combustion of the fuel and finally expansion and then the same cycle begins again. 9. MECHANISM FOR TRANSFORMING RECIPROCAL MOTION INTO ROTATIONAL OR VICE VERSA AND APPLICATIONS THEREOF is characterized by, the application of the mechanism, according to claim 6 or 7, a clutch arrangement in which a shaft (6) is connected through a sliding groove, to the second annular component (3) functioning as a rotor, wherein the third annular component (2) is firmly connected to a component (4), wherein a mechanism can exert an axial force (F) on the first annular component (1), forcing the first and third annular components (1, 2) to move closer to each other, in which case the second annular component (3) is immobilized between the first and third annular components (1, 2) , after which the rotation of the shaft (6) is fully transferred to the component (4), on the other hand, if the axial force (F) on the first annular component (1) ) is lifted by the mechanism, it moves back to its initial position , when the second annular component (3) will be released and begin to move again, sliding between the first and third annular components (1, 2) and therefore transferring rotation from the shaft (6) to the element (4) will be interrupted, where in the first and third annular components are optionally connected to an outer casing (7), the first annular component with axially sliding wedges (14) and the third annular component with the possibility of only slight rotation. 10. MECHANISM FOR TRANSFORMING RECIPROCAL MOTION INTO ROTATIONAL OR VICE VERSA AND APPLICATIONS THEREOF is characterized by, the application of the mechanism, according to claim 6 or 7, in a differential arrangement comprising two symmetric mirror image sections, each consisting of a second annular component (3), functioning as a rotor, connected to a shaft (6) by means of a sliding groove, a first annular component (1), a third annular component (2), a mechanism that exerts the necessary force (F) on the first annular component (1) to sufficiently approach the third annular component (2), trapping and immobilizing the second annular component (3) between the first and the third annular component (1, 2), so that the third annular component (2) is engaged and moves simultaneously towards the shaft (6), wherein each of the two annular components (2) is firmly connected to a toothed belt (15), moving through a shaft (11) through a cooperating toothed belt (12), so that, as long as the resistance of two axes (6) during movement is the same, the second annular components (3) remain in engagement with the third annular components (2 ) and the rotation of the toothed belt gear (15) is transferred in its full effect to the shafts (6); on the other hand, if the resistance increases in one of the axes (6), the corresponding first annular component (1) will move back slightly, the corresponding second annular component (3) will be released and begin to slide between the first and third annular components ( 1, 2), after which the number of rotations of the corresponding shaft (6) will be reduced until the balance of the shafts (6) and the resistances are restored and their number of rotations is equalized, whereby each first annular component (1 ) is optionally connected to a body (7) using axial sliding (14) and every third annular component (2) is connected to the body (7) being capable of circumferential sliding. 11. MECHANISM FOR TRANSFORMING RECIPROCAL MOTION INTO ROTATIONAL OR VICE VERSA AND APPLICATIONS THEREOF is characterized by, the application of the mechanism, according to claim 6 or 7, a device that increases / reduces the number of rotations in which a mechanism stops transformation of rotational motion into reciprocal motion, or vice versa, with n = n1 number of crests/valleys, in which a first and a third annular components (1, 2) function as stators and are firmly mounted in a body (7), while the second annular component (3) functions as a rotor firmly connected to a piston (4), rotating and reciprocating axially and moving along a shaft (6) with a grooved slide, it is coaxially connected to another similar mechanism, with the same reciprocity path (L) and a number of crests and valleys n = n2 + ni, by means of pistons (4) and coupling pin (19) in order to allow rotation in relation to each other, but not displacement axial, in which if the axis (6) of the first mechanism rotates with Ni rotations, the axis (6) of the second mechanism will rotate with rotations N2 = Ni x (ni/n2), that is, the pair of mechanisms works as a device reducing and increasing rotational speed. 12. MECHANISM FOR TRANSFORMING RECIPROCAL MOTION INTO ROTATIONAL OR VICE VERSA AND APPLICATIONS THEREOF is characterized by, the application of the mechanism, according to claim 6 or 7, a device that increases / reduces the number of reciprocations in which a mechanism stops transformation of rotational motion into reciprocal, or vice versa, with n = ni number of crests/valleys, in which a first and a third annular component (1, 2) function as stators and are firmly mounted in a body (7), while the second annular component (3) functions as a rotor firmly connected to a piston (4), rotating and reciprocating axially and moving along a shaft (6) with a splined slide, it is coaxially connected by the shafts (6) and a coupler (20) with wedges (14) tightly to another similar mechanism, with a different number of crests/valleys n = n2 + ni, when the pair of mechanisms functions as a device increasing/reducing the reciprocating speed and/or the reciprocating path lengths if the reciprocating path (Li) of one mechanism is different from the reciprocating path (L2) of the other. 13. MECHANISM FOR TRANSFORMING RECIPROCAL MOVEMENT INTO ROTATIONAL OR VICE VERSA AND APPLICATIONS THEREOF is characterized by the application of the mechanism, according to claim 6 or 7, in coupling an electric motor (E) to two similar motors (M ) with cylinders according to claim 8 or 9, the axes of which (6) coincide with the axes of their cylinders, wherein the bodies of the motors M are mounted coaxially on the body (stator) of the electric motor E: one on the right and another on the left, in which the rotor shaft of the electric motor (E) is abolished and replaced by the shafts (6) of the two motors (M), and in doing so, they are synchronized with each other, resulting in piston operation moving in opposite directions so that the inertial forces of reciprocity balance. 14. MECHANISM FOR TRANSFORMING RECIPROCAL MOTION INTO ROTATIONAL OR VICE VERSA AND APPLICATIONS THEREOF is characterized by the application of the mechanism, according to claim 1, 2, 3 or 5, a two-cylinder engine, where each cylinder operates with a pair of annular components with wavy surfaces that transform motion on their adjacent sides, the cylinders are coaxial, mounted in a mirror image arrangement, with components moving in opposite directions, functioning as pistons (4) to balance the inertial forces of reciprocity, in which each cylinder comprises a first annular element (1) functioning as a stator and a second annular component (3) functioning as a rotor, firmly connected to a piston (4), wherein stators (1) are firmly connected to each other another and with a common body (7), in which each rotor (3) supports an external rack (recoil) cooperating with a toothed belt (12) of a pair of wheels mounted on a common axis (11) parallel to the longitudinal axis of the cylinders, in which the pair of toothed belts (12) synchronize the rotors (3) and transfer motion to the shaft (11), after which a force is exerted on the pistons (4) as they move between TDC and BDC , due to the pressure of the working fluid and/or the assistance of the traction spring (21), thus keeping the corrugated surfaces of the rotors (3) in contact with the corresponding stators (1), where the traction spring (21) connects the pistons (4) to each other through openings in the stators (1) and acts to assist their recovery, keeping the rotors (3) in continuous contact with the corresponding stators (1), which is particularly important during the period in which the engine is not operating, thus ensuring synchronization, in which each cylinder comprises traditional valves or valves with ports or valves (18) that are controlled with the disc-shaped camera (13) and rods (17). 15. MECHANISM FOR TRANSFORMING RECIPROCAL MOTION INTO ROTATIONAL OR VICE VERSA AND APPLICATIONS THEREOF is characterized by the application of the mechanism, according to claim 6 or 7, a piston engine cylinder, comprising a first and a third component annular component (1,2) functioning as stators and a second annular component (3) functioning as a rotor, in which the stators (1,2) are firmly connected to a common body, in which the rotor (3) plays the role of the piston and the working fluid flows between the stators (1, 2), rotor (3) and the common body, using valves with openings in the rotor (3) or conventional / classic valves (18) in the common body and, in the case of traditional valves (18) also using a disc-shaped camera (13) and rods (17), also, in the common body. 16. MECHANISM FOR TRANSFORMING RECIPROCAL MOTION INTO ROTATIONAL OR VICE VERSA AND APPLICATIONS THEREOF is characterized by, the application of the mechanism, according to claim 6 or 7, a two-cylinder, double-acting piston engine, in which the cylinders are coaxial, assembled in a mirror image arrangement, with components moving in opposite directions to balance reciprocal inertial forces, wherein each cylinder comprises a first and a third annular component (1,2) functioning as stators and a second component annular (3) functioning as a rotor, moving through a groove of a common shaft (6) coinciding with the axis of the piston engine cylinder, in which the stators (1, 2) are firmly connected to a common body cylindrical (5/7) and, in addition, the stators (2) are connected to each other, in which the rotor (3) plays the role of the piston and the working fluid flows between the stators (1, 2), rotor ( 3) and cylindrical casing body (5/7), wherein valves with openings are provided in the rotor (3) and cylindrical casing body (5/7) or conventional/classic valves (18) in the cylindrical casing body ( 5/7) and, in the case of traditional valves (18) using a conventional camshaft or controlled with disc-shaped cam (13) and rods (17), also, in the cylindrical casing body (5/7) .