The invention refers to a device for increasing the efficiency of any rotary power generating system with progressive variation, applicable in any industrial field, which aims to optimize fuel consumption by continuously changing the transmission ratio from the input motor shaft to the output shaft.

There are known gearboxes applicable to motor vehicles, with the modification of the transmission ratio in steps; they present the disadvantage that, due to the limited number of steps, the adaptation of the motor moment, whose variation is small, to the resistant moment, which has a very large variation, is discontinuous, which contributes to the decrease in dynamic qualities and the increase in fuel consumption.

Variable transmission gearboxes are also known, which have the disadvantage of using drive belts that determine both a limited mode of operation and limited mechanical parameters.

Also known is the gearbox according to US patent 3447398 A, which refers to a torque converter interposed between a drive shaft and a driven shaft, having a drive gear rotary around a primary axis and being in connection with some planetary gears rotary around second axes parallel to the primary axis; the planetary gears being coupled with eccentric weights also rotary around the secondary axes in a predetermined phase relationship; the planetary gears and weights being coupled to a driven gear with which either one or a pair of pinions can be selectively connected; each pinion being provided with a one-way clutch engageable with a torque shaft with limited rotation and essentially fixed; clutches operating in opposite directions; preferably both the drive shaft and the driven shaft, as well as the torque shaft, being fitted with torque dampers to smooth torque variations.

A gearbox is also known according to patent F 1588205 which refers to an automatic speed and torque converter with continuous variation, made up of a hypocycloidal planetary gear, whose internal gear ring has been removed, as a result the device remains composed of - a satellite drive motor shaft, driving a satellite that meshes with a central pinion to be mounted on the output shaft, this satellite having a mass with a determined weight fixed to its periphery; the whole assembly rotating uniformly, with a determined and uniform input torque, so that if there is an increase in the resisting torque on the output shaft, this increase will result in a proportional decrease in the speed of this shaft, and consequently in a speed difference between input and output shafts; the difference in speed will cause the satellite to rotate on itself; in this rotation of the satellite, the mass attached to it will sometimes approach, sometimes move away from the axis of rotation of the apparatus, and therefore its circumferential velocity will vary in proportion to its distance from this axis. At the moment of mass speed increase, the consequent increase in force will require an increase in power that will be automatically taken at that moment from the engine torque, then at that moment of mass speed reduction, it will be restored to the output shaft from which it will end up increasing the torque to compensate for the increase in resistive torque produced on this shaft by reducing the speed as stated. This transfer of energy from the motor shaft to the mass output shaft and this conversion of speed into torque varies proportionally to the difference in speed of the two shafts with the following characteristic points: a) If the speeds of the two shafts are equal, the satellite will not spin and no speed to torque conversion occurs, b) If the speed of the output shaft drops to zero, that of the input shaft always remaining the same, then the entire speed is converted into a torque, the output torque becomes infinitely large, but no power is available on this output shaft, its speed being zero. The device then acts as a clutch, c) If the speed of the output shaft becomes greater than that of the input shaft, and therefore the torque less than that of this shaft, the satellite and its mass will start themselves, but in the opposite direction than before, the extra power then being converted into speed to compensate for the difference in speed between the two shafts instead of being converted into torque as in the previous case, d) Finally, instead of reducing the speed to zero, the output shaft can also rotate in the opposite direction, thus automatically giving a reverse direction if desired. All these speed and torque variations are done automatically without the need to use any control device, the machine acting exactly like a kind of rotary torque rocker. On the other hand, considering the irregularity of the torque transmitted by the mass to the output shaft, 4 planetary gears instead of one are mounted on the periphery of the pinion and 4 masses instead of just one, these 4 masses being placed on the periphery of the satellites so that the forces transmitted by them to balance each other, the resulting total force on the output shaft being then perfectly regularized. The transmittable power capacity of the device is then quadrupled. These satellites and these masses can also be 3, 6, 8 or more in number depending on the requirements, provided that the forces transmitted to the output shaft are balanced between them. Other types of differential gears may be used, provided they allow the fundamental principles of the device to be applied. This device applies to automobiles, machine tools, tractors, motorcycles, railways, etc.

All these solutions present the disadvantage that they do not use the principle of energy accumulation in the steering wheel, as well as the disadvantage that they only use part of the generated force.

A planetary gear box with progressive variation is also known according to patent RO 12966 A2, which allows continuous modification of the transmission ratio. Due to the fact that the direction of rotation of the inner box is the same as the direction of rotation of the eccentric pinions, the disadvantage arises that the mechanism introduces an additional mass moment of inertia, which translates into additional resistance to rotation, which induces additional consumption of fuel; In addition, the use of conical pinions to create the mechanical system induces an additional cost and an increase in the complexity of the adjustment during assembly.

The technical problem that the present invention solves is to decrease the fuel consumption required for the operation of an engine.

The technical problem is solved by the invention by making a device for increasing the efficiency of any rotary power generating system with progressive variation that has the primary motor shaft (input) inertial-centrifugally coupled to the secondary (output) shaft. This inertial-centrifugal coupling ensures an independent movement of the shafts and eliminates the disadvantages presented in the inventions listed in the previous paragraph, by eliminating the mechanical couplings between the shafts. Also, by using the flywheel effect and the full use of the force generated, this invention practically increases the efficiency compared to those present in the above reference inventions.

The advantages of this invention are numerous:

- the field of applicability of this device is vast, starting from the vehicle industry to any of the branches of the industry where continuous change of speed is needed.

- Reduces power losses to a greater extent than conventional automatic transmissions, improving efficiency and acceleration, by keeping the engine speed constant; - Automatic adaptation, dynamically, of the moment of exit from the device, to the same amount of fuel of any kind;

- Improved dynamics due to the lack of traction force interruption;

- Improves dynamic and energetic performances in transient regimes;

- Improving driving comfort by automating clutch engagement and by not needing to change transmission ratios;

- Improving the control of polluting emissions and reducing the noise level.

Below is an example of a device for increasing the efficiency of any rotary power generating system with progressive variation, with reference also to figures 1 to 7, which represent:

- Fig. 1 - longitudinal section through the device for increasing the yield of any rotary system generating power with progressive variation, with the indication of the moments and revolutions at idle;

- Fig. 2 - explanation of the mode of operation in the situation where the output shaft is acted upon by a resistive moment, MR1 , which completely blocks (MR1 = Ml) its movement;

- Ftg.3 - explanatory on the mode of operation in the situation where the output shaft is acted upon with a resistive moment MR2 smaller than MR 1 , the output shaft rotary with a revolution t' 1 1 < 11 of the input shaft

- Fig.4 - view from X; the position of the eccentrics when idling;

- Fig.5 - view from X; the position of the eccentrics in the situation where the output shaft is acted upon with a resistive moment MR2 smaller than MR1 , the output shaft will rotate with a revolution t'l l < tl of the input shaft and will transmit, through the unidirectional bearing, a movement of rotational speed t6 < tl on the intermediate pinion which will transmit movement, through the pinions, to the eccentrics which, through their rotational movement, will create an oscillating moment of inertia, Mo

- Fig.6 - view from X; the position of the eccentrics in the situation where the output shaft is acted upon with a resistive moment MR2 smaller than MR1 , the output shaft will rotate with a revolution t'l l < tl of the input shaft and transmit, through the unidirectional bearing, the direction conversely, a rotational motion of speed t6 < tl on the intermediate pinion which will transmit motion, through the pinions, to the eccentrics which, through their rotational motion, will create an oscillating moment of inertia, Mo - Fig.7 - partial view of the pinions in box C (solution with two pinions)

An example embodiment of the invention is given below, which according to fig. 1, consists of an assembled inner box, A, which is assembled axially in an assembled outer box, B, to which an assembled side box is axially fixed, C; assembled inner box, A, made of a primary drive shaft, 1, having a flange, by means of which the shaft is oriented and fixed on a cover, 2, in which, axially, a bearing , 3, is assembledand radially, in some bosses, a, processed cylindrically, some bearings , 4, are fixedly assembled in which, with a shoulder, conventionally right, some satellites, 15, are assembled, each of which, on a median shoulder, has assembled a bearing, 4* ; axially, in the bearing, 3, an intermediate pinion, 6, is assembled, which, to the left of its toothed crown, has a second bearing assembled, 18; in some bearings, 19, (fig. 4) which are fixed in the cover, 2, some pinions, 14, are assembled, which mesh both with the pinions, 15, and with the toothed crown of the intermediate pinion, 6; on the cover, 2, and oriented on the bearings, 4’, 18 and 19, an intermediate cover, 5, is centered, which is firmly fixed to the cover, 2, by some screws, 13; on the cover, 5, being oriented and fixed a cylindrical wall, 2ft; on the conventional left side of each pinion, 15, one eccentric, 16, is fixed rigidly (fig. 1 , fig. 4, fig. 5, fig. 6); after each eccentric, 16, on each pinion, 15, is assembled a bearing, 4"; on each bearing, 4", it is oriented, and on the cylindrical wall, 20, another cover, 21, is oriented and fixed, in the center of which is assembled a bearing, 22, through which the intermediate pinion, 6, slides; assembled box, B, consisting of a cover, 23, oriented by means of a bearing, 24, on the primary motor shaft, 1, from the assembled inner box, A, cover, 23, on which it is oriented and fixed by means of screws, 25, with the conventionally right surface, an external cylindrical wall, 26, from which, on its conventionally left surface, a cover, 27, is oriented and fixed, by means of screws, 28; cover, 27, which is oriented by means of a bearing, 29, on the primary motor shaft, 1, and which, radially, has some bearings, 35, assembled; a spacer, 30, is interposed between the bearing, 22, and the bearing, 29, on the primary drive shaft, 1; after the bearing, 29, another spacer, 31, is assembled after which a unidirectional bearing, 7, then another spacer, 32, are assembled; assembled side box, C, consisting of a side cover, 36, provided with an axial hole, e, in which is mounted a bearing, 34, in which is assembled the output shaft, c, of a pinion, 11, in which a oneway bearing, 12, which works in the opposite direction to the one-way bearing, 7, can be fixedly assembled; radially, on the same diameter on which the bearings are arranged, 35, but in the mirror, inside the side cover, 36, in some bosses, st are mounted some bearings, 35’, in which some intermediate pinions, 9, can be assembled, which engages with third pinions, 10, also assembled in some bearings, 37, not shown in the figure, fixed radially in the side cover, 36; this assembled side box, C, is oriented, by means of the bearing, 12, assembled in the pinion, 11, on the primary motor shaft, 1, and, by means of the intermediate pinions, 9, in the bearings, 35, and, by means of the third pinions, 10, in some bearings, 37*, assembled in the cover, 27, and fixed to the cover, 27, by means of screws, 38.

Mode of operation

According to fig.1 , by acting from the motor with a moment, Ml, at a revolution, tl, on the input shaft, 1, at idle, it acts on the assembled box, A, which, by means of the inertial coupling consisting of the pinions, 15, on which the eccentrics, 16, are fixedly assembled, and which drive the pinions, 14, which drive the intermediate pinion, 6, which rotates at the same speed, tl, and in the same direction as the input shaft, 1, actuate the one-way bearing , 7, on which is fixed the pinion, 8, which engages the intermediate pinion, 9, which drives the third pinion, 10, which actuates the output shaft, 11, because the one-way bearing, 12, is mounted in the opposite direction to the oneway bearing, 7; the eccentrics, 16, will remain motionless; the output shaft will rotate with the same speed, tl, but in the opposite direction; this would be the situation in which, for example, a car would go downhill, without brakes, with the engine running at tl speed, and the wheels would take over the movement corresponding to this speed, without resistance; According to fig.2, in the situation where the output shaft, 11 , is acted upon by a resistive moment, MR1, which completely blocks (MR1 = Ml) its movement; on the input shaft, 1 , acting with the same moment, Ml, at the same speed, tll(MRl) = tl, by means of the unidirectional bearing, 12, the intermediate pinion, 6, and, as a result, the pinions, 14, are locked they will drive the pinions, 15, which will drive the eccentrics, 16, these creating a moment of inertia Mexc; as a result, the eccentrics, 16, will rotate symmetrically, with a maximum speed, texemax ; this would be the situation where, for example, a car would have revved the engine at speed tl and braked completely; According to fig.3, in the situation where the output shaft, 11, is acted upon with a resistive moment MR2 smaller than MR1, the output shaft, 11, will rotate with a revolution, t’ll < tl, of the input, 1, and will transmit, through the one-way bearing, 12, a rotational movement of speed t6 < tl on the intermediate pinion, 6, which will transmit movement, through pinions, 14 and 15, to the eccentrics, 16, which, through the movement their rotation, will create an oscillating moment of inertia, Mo, according to frg.5 and fig.6, which, through the same pinions, 15 and 14, will transmit the oscillating moment, Mo, to the intermediate pinion, 6, which will act alternately on the one-way bearings, 7 and 12, so that, at the output pinion, 11, a continuous rotational movement will result, with the same speed, t’ll (MR2); At a complete rotation of the pinion, 15, with the eccentric, 16, due to their relative rotation movement with respect to the intermediate pinion, 6, in the first half of rotation (fig.4), a first moment of inertia is created which binds the intermediate pinion , 6, to have a movement in one direction; and in the second half of rotation (fig. 5), a moment of inertia of the opposite direction is created which forces the intermediate pinion, 6, to move in the opposite direction; after the cessation of action with the resistive moment, MR1, due to the centrifugal force acting on the eccentrics, 16, they will return to the radial axial equilibrium position, according to fig-3.