Field of the technique

The present invention refers to the field of the transmission systems, in detail concerning a gear-box transmission system.

Background art

In the field of cinematics, whose work is based on the principles of the lever, the ratio between the active force and the road traveled is proportion and this ratio cannot be changed. This unchangeability is conditioned by various technical options.

It is very well known that increasing the active force, the road traveled reduces and, on the contrary, increasing the road traveled, the active force is reduced. The active force determines the maximal road traveled as well as the time necessary thereto. Today, when wanting to increase the maximal road traveled, it is compulsory to increase the active force.

The scope of the present invention is therefore to describe a gearbox transmission system which solves the aforementioned drawbacks.

Summary of the invention

According to the present invention it is realized a gear-box transmission system, characterized in that comprises at least a first and a second shaft respectively of input of a driving force and output of the driving force, said first shaft being joint to a first gear meshing with a second gear in turn meshing within a planetary or inner teeth gear whose rotation axis is offset with respect to the rotation axis of said first gear; said second gear transmitting the rotation motion towards said second shaft through eccentric meshing means with respect to said rotation axis of the first gear; and wherein the assembly formed by the first gear the second gear and the planetary or inner teeth gear and/or the eccentric meshing means cause a variation of the ratio of rotation speed between the first and the second shaft such as said second shaft rotates with a lower speed with respect to first shaft. In detail the rotation speed ratio is preferably 1:3.

In detail, the meshing means comprise a support provided with an axial hole being eccentric with respect to said axis X.

Advantageously, said eccentric meshing means comprise at least a fourth gear solidly rotating with said second gear and positioned at a predefined distance from said second gear along a rotation axis thereof, and comprise at least a fifth gear, meshing with said fourth gear and solidly jointed to said second shaft.

Advantageously, said eccentric meshing means comprise furthermore a rod discoid spacing element, having a first hole along said first rotation axis for the passage of said first shaft and a second hole along said second rotation axis for the passage of a junction shaft between said second gear and said fourth gear. Advantageously, said discoid spacing element comprises for each hole friction reducing rolling means, each one introduced within said hole and laying outside of the respective shaft.

Said rolling means can be alternatively replaced by bushes.

Said fifth gear meshes on a gear wheel with inner teeth that is fixed on the box of the system.

Advantageously, said first planetary or inner teeth gear is solidly jointed to a third gear having a rotation axis coinciding with the rotation axis of the first planetary or inner teeth gear itself.

Advantageously, said third gear and said first planetary or inner teeth gear present a hole in correspondence of the their own rotation axis for the passage of a portion of engagement of an eccentric element with connecting rod transferring the motion towards a secondary shaft jointed thereto and rotating on an own axis. Advantageously, said secondary shaft presents a rotation axis coinciding with the rotation axis of said first shaft.

More in detail, said first shaft and the second shaft are coaxial.

In detail said third gear engages within a second planetary or inner teeth gear. In particular, said fourth gear engages on a third planetary or inner teeth gear. Advantageously, said second and third planetary or inner teeth gear are solidly jointed to a box or container enclosing said gears, and from which said first and second shaft depart outwardly in correspondence of output holes provided on the box or container itself.

Advantageously, said shaft secondary is coaxial with said first shaft.

Finally, the first shaft and said second shaft are installed on means reducing the rolling friction that are installed on a box or container.

Description of the annexed figures

The invention will be now described in a preferred and non-limiting embodiment referring to the annexed figures and wherein:

- figure 1 a perspective exploded view of the a gear-box transmission system object of the present invention;

- figure 2 shows a section exploded view of the system of figure 1;

- figure 3 shows a section view of the system of figure 1 when in a configuration actually mounted;

- figure 4 and figure 5 respectively illustrate a section view and an exploded view of a engineered embodiment of the gearbox transmission system. Detailed description of the invention.

Referring to the annexed figures, the present invention shows in detail a gear-box transmission system.

In detail inside of a box or container 20, a plurality of gears having different ratios is enclosed. More in detail, from a box or container 20 a first shaft la rotating around an own rotation axis X perpendicular to the wall of the box or container 20 comes out. The first shaft la represents the shaft of input of the driving force.

The shaft la is jointed in correspondence of the end which is opposed with respect to that the comes out from the box or container 20 with a first gear 1, meshing with a second satellite gear 2, laying substantially on the same plane of rotation, and therefore mechanically coupled to laterally with respect to first gear 1. The second gear 2 presents an own rotation axis Y, parallel to the axis X but laterally shifted with respect to this last.

The second gear 2 meshes furthermore on the inner crown 3i of a planetary or inner teeth gear 3, that presents a C-shaped stretched section wherein the inner crown 3i presents meshing means and rests on a first side of the central portion 3c, which in contrast detects a solid wall. The inner crown 3i lays therefore on a plane which is parallel to the plane of the central portion 3 c, but anyway is distinguished to this last in such a way that in use the second gear which presents a wall in substantial proximity of the central portion 3 c, even without touching it. On the side opposed with respect to the one wherein there is the inner crown 3i, a third gear 4, laying on the same plane of the central portion, is jointed to the central portion 3c. In detail, the third gear 4 is pivoted on a supporting pin of a junction element 9 with a second planetary or inner teeth gear 10, which is fixed on the containment box of the assembly.

The junction element 9 that is rod-shaped presents an element axially engaged into a central hole of the planetary or inner teeth gear 3. In detail, the first planetary or inner teeth gear 3 presents an own rotation axis Z, parallel to the axis X and the axis Y, but distinguished with respect to those last ones. The third gear 4 is positioned so as to have its center within in correspondence of the rotation axis of the first planetary or inner teeth gear 3. The junction element 9, which represents an eccentric rod or eccentric element, presents an own shaft 9a (secondary shaft) output that protrudes from the box or container 20 on the side opposite to the one where the first shaft la comes out. The shaft 9a of the junction element presents an own rotation axis coaxial to the axis X of rotation of the first shaft la.

Furthermore, the third gear 4 meshes furthermore on the inner crown lOi of a second planetary or inner teeth gear 10, that presents a C-shaped section stretched wherein the inner crown lOi presents meshing means and rests on a first side of the central portion 10c, which in contrast detects a solid wall, provided with a central hole for the passage of the shaft 9a of the junction element.

The inner crown lOi lays therefore on a plane which is parallel to the plane of the central portion 10c, but anyway distinguished from this last in such a way that in use the third gear presents a wall in substantial proximity of the central portion 10c, even if without touching it. Furthermore, central portion 10c is rendered solidal to the box or container 20, in such a way that it reacts of the torque exerted of the third gear 4 forcing this last to eccentrically rotate with respect to the shaft 9a, and in detail to rotate on the inner crown lOi.

The shaft 9a passes through the box or container 20 in correspondence of the hole wherein there is a ball or roller bearing 11 for reducing the rolling friction during the rotation of the shaft 9a itself.

Inside of the box or container 20 is furthermore comprised a partition element 8, provided with a couple of holes allowing the passage of the first shaft la and of a command shaft 2a of the second gear 2. The command shaft 2a is so defined because through it the driving force of rotation that then is distributed on the output shafts 6a, 9a enters in the system of the present invention.

On both the holes there are ball or roller bearings 13, 14 for allowing to reduce the reciprocal friction of rotation between the shafts and the partition element 8. Alternatively, the ball or roller bearings, that realize revolving means, are interchangeable with bushes.

Hence, the partition element 8 acts as a spacing discoid element for supporting the aforementioned gears. More in detail, the partition element 8 comprises a secondary hole 8f that is eccentric with respect to X axis.

In detail the first and the second gear 1, 2 lay on of a first side of the partition element 8 while on the second side of the partition element 8 is present a fourth gear 5 within which is settled the command shaft 2a passing through the partition element 8.

The fourth gear 5 actuates in rotation a fifth gear 6 rotating on a plane which is parallel to the one of rotation of the fourth gear 5 and being it also positioned on the same side of the partition element 8.

The fourth gear 5 presents a rotation axis coinciding with the axis Y that passes for the secondary hole 8f. The fifth gear 6 and the fourth gear 5 lay on parallel planes and on the same side of the partition element.

The fifth gear 6 comprises a hole passing both on it and on the respective command shaft 6a solidly jointed thereto.

The command shaft 6a represents a second shaft of the system object of the present invention, and in detail is a output shaft of the driving force.

Therefore, both the fifth gear 6 and the associated command shaft 6a are hollow; within the cavity which is created it is made pass the first shaft la, which is solidly hinged to the first gear 1; the shaft la is therefore long sufficiently to pass through the partition element 8 and the assembly formed by the fifth gear 6 and the command shaft 6a associated thereto. Consequently, the fifth gear 6 wheel being it also on the same axis X of rotation of the first gear.

Also the command shaft 6a comes out of the hole present on the body of the box or container 20, and makes it passing through ball or roller bearings 15 for reducing the rolling friction during its rotation and also passing through the hole of the central portion of a third planetary or inner teeth gear 7, which is rigidly jointed to the box or container 20.

The third planetary or inner teeth gear 7 presents a stretched C-shaped section wherein the inner crown 7i presents meshing means and rests on a first side of the central portion 7c, which in contrast defines a solid wall provided with the hole for the passage of the first shaft la and of the command shaft 6a. The fourth gear 5 in detail meshes also with the inner crown 7i.

The gears of the transmission system object of the present description are configured in a precise dimensional ratio. In detail, in fact, once defined with the number 50mm the size of the first gear 1, the size of the second gear 2 is equal to 100mm (that is, it will rotate around itself with a rotation speed equal to 1/3 with respect to the rotation speed assumed by the first gear 1) while the first planetary or inner teeth gear 3 presents a size equal to 200, therefore rotating around the axis X with a rotation speed assumed by the second gear 2.

Furthermore, the third gear 4 solidly jointed to the first planetary or inner teeth gear 3, will have therefore the same rotation speed of this last, anyway having a dimensional ratio equal to 50mm resulting therefore of the same size of the first gear 1.

The second planetary or inner teeth gear 10 presents a dimensional ratio equal to 100mm, and this implies that there is no difference of relative speed of rotation between the third gear 4, that acts as a satellite on the second planetary or inner teeth gear 10. The fourth gear 5 presents the same size of the first gear 1 (that is, 50mm), while the fifth gear 6 results in size equal to 100mm, consequently rotating with a rotation speed equal to the rotation speed that assumes the fourth gear 5 since it is constrained between the second planetary 7 and the fifth gear 5 itself. Also the third planetary or inner teeth gear 7, equivalently to of the first planetary or inner teeth gear 3, presents a size equal to 200mm.

With said dimensional ratios, while rotating the first shaft la with a speed for example equal to 9rpm, the rotation of the second gear 2 takes place at 3rpm, and the same applies for the fourth gear 5. This last, meshing on the fifth gear 6, transfers therefore the motion to the command shaft 6a with a rotation speed at 3rpm, always thank to the presence of the planetary of inner teeth 7 that is fixed on the box 20.

Equivalently the transmission of the second gear 2 towards the first planetary or inner teeth gear 3 causes a reduction of the rotation speed of 1/3; consequently the first planetary or inner teeth gear 3 will rotate with a rotation speed equal to 1 rpm that is therefore the rotation speed of the third gear 4, by virtue of its solidal union with the respective planetary or inner teeth gear 3. The eccentric union with the junction element 9 causes that also the second shaft 9a rotates at the same speed of 1 rpm.

With the transmission system object of the present invention, both the first shaft la and the command shaft 6a rotate they all in a same concordant direction, as also the second shaft 9a does.

In use, therefore, the combined motion of the second gear 2 with the first planetary or inner teeth gear 3, exerts a coupling force. This force is equal to the double of the active force of the second satellite gear 2, and it is transmitted to the command shaft 6a of the fifth gear 6 out of the box or container 20.

As a consequence of the individual and simultaneous rotations of the second gear 2 (primary satellite gear) and of the planetary or inner teeth gear 3 (secondary satellite gear) it is obtained, further than the coupling force, also a prolonged stroke of the active force. The force moving the secondary satellite gear, is transmitted to the second shaft 9a by means of the junction element with the connecting rod 9.

Advantageously, with the prolonged stroke of the active force, that is exempted by losses, it is possible to use the reactive force in a different and more efficient way with respect to the mechanisms used up today. The prolonged stroke changes the angular and linear speeds of the gears inside the mechanism, which are no longer proportional to the speed of the first shaft la from which the driving force comes.

The active forces on both the primary satellite gear (second gear 2) and secondary gear (planetary or inner teeth gear 3) have same direction and this equivalent direction of the active forces that are present, allows to modify the ratio between the active force and the traveled road that was not changeable up to here. This new ratio of proportionality between the first shaft la and the second gear 2 (primary satellite gear), that bases itself on the third principle of dynamics; this allows, with a given initial active force, the usage of higher reactive forces with respect to the systems today in use.

In the case where the linear and angular speeds of the command shaft 6a and those of the first shaft la are the same, the force on those two shafts would result different. Conversely, if the forces on the command shaft 6a and those on the first shaft la are the same, the angular and linear speeds of the two shafts would not be the same. The results (force and angular speed) that are obtained but the primary satellite gear, considering the circumference deriving by its own rotation and also considering that we are dealing with rotation forces, would not be possible without the introduction of the planetary or inner teeth gear 3.

Resuming, into the mechanism shafts and gears work in fact as a dependent couple, but are divided di two functional groups that work independently one from the other. The first group of gears provides the active force, increased of 100%, towards the shaft that exits from the front part of the mechanism. The second group of gears transforms the reactive force in the active one, and brings it towards the shaft that exits out of the rear shaft of the mechanism increasing it of 400%.

The second group of gears has a double function: the first, is to transform the reactive force in the active one and, the second, is to prolong the road travelled for the first group of gears. A first shaft with a gear brings the active force into the mechanism. Outside the mechanism, two shafts exit, one on the front part and one on the rear part. Those two shafts can works as independent shafts and eventually can be coupled also on a single shaft, using mechanical couplings of a known type outside the box 20.

It has to be noted that the three shafts rotated in the same direction and find themselves on the same axis.

By observing the system object of the present invention it is possible to distinguish a front part and a rear part each one representing a respective first, second group of gears.

Of the first group of gears are part: a gear 1 of the driving shaft with diameter of 50mm, a primary satellite gear 2 with diameter 100mm with shaft and smaller gear 5 of 50mm on the other side of the shaft. The lever 8 that brings the primary satellite gear with diameter of 100mm and the small gear 5 with diameter 50mm. The fixed gear 7 of diameter equal to 200mm around which the smaller primary satellite gear 5 rotates. The front shaft with the associated gear 6 with diameter equal to 100mm.

The second group of gears, the one of the rear part, comprises: a gear of the driving shaft with diameter of 50mm, a primary satellite gear with diameter of 100mm that is connected between the first and the second. A secondary satellite gear 3 with diameter of 200mm with a smaller gear 4 with diameter of 50mm on the rear wall. A fixed gear 10 with diameter 100mm, that determinates the number of revolutions for the small secondary satellite gear 4, and an eccentric element 9 that keeps the secondary satellite gear.

In detail, furthermore, all the three shafts (first gear la, second shaft 6a and third shaft 9a) are rotating on the same axis X.

The operation of the first group of gears takes place as follows: the gear 1 of the driving shaft with diameter of 50mm, moves the primary satellite gear 2 with the shaft and the smaller gears 5 on the other side of the shaft.

The primary satellite gear 2 with diameter of 100mm with the reactive force moves the secondary satellite gear 3 with diameter of 200mm and brings the active force multiplied by four towards the smaller gear with diameter of 50mm rotating in clockwise direction.

The secondary satellite gear rotating and revolving respectively around and with respect to the fixed gear 10 with diameter 100mm in clockwise direction, allows a 50% prolonged traveled road for the primary satellite gear with diameter of 100mm with the shaft and the smaller gear of 50mm.

The lever that brings the primary satellite gear with the shaft and the smaller gear allows for a rotation around the central axis by rotating in anticlockwise direction.

The primary satellite gear 2 with diameter 100mm with its smaller gear of 50mm rotates in clockwise direction around the fixed gear with diameter of 200mm and moves the gear 6 of diameter of 100mm with the front shaft.

The gear of the front shaft with diameter of 100mm rotating in anticlockwise direction, brings the active force, doubled, outside the system object of the present invention.

For what deals with the rear part, and hence the second group of gears, the gear with diameter of 50mm of the driving shaft brings the active force and moves the primary satellite gear with diameter of 100mm. This last, moves the secondary satellite gear 3 with diameter of 200mm. The secondary satellite gear 3 with the smaller gear 4 of 50mm rotates around the fixed gear 10 with diameter of 100mm, revolving around the axis X, rotating in clockwise direction. The secondary satellite gear transforms the reactive force in the active force and moves the rear eccentric shaft that supports this secondary satellite gear.

The rear eccentric shaft brings a part of the reactive force, transformed in active force, outside the system which is object of the present invention.

By taking a look to the first group of gears, in fact, the gear of the motor having diameter equal to 50mm, that performs 9 turns and meshes on the primary satellite gear of diameter 100mm that performs 3 turns for a revolution path of 360° around the axis X. Between those two, the ratio of the number of turns is 9:3, the linear speed of the driving gear is l,413m/s and the linear speed of the primary satellite gear is 0,922m/s. The ratio between those two speeds is equal to 1: 1,5. In this case the forces ratio is 1:2.

The traveled path of the satellite gear that brings the active force is therefore prolonged of 50%.

Figure 4 and figure 5, as already anticipated, provide a view respectively in section and exploded of an engineered embodiment of the system object of the present invention.

The embodiment of figures 4 and 5 does not differ in principle with respect to the previously described one, but represents a more engineered solution thereof. Therefore, all the advantages and technical effects previously described are still valid also for the new embodiment herewith being described.

In detail, also for the embodiment of figures 4 and 5, the box 20 is always present, but the third planetary of inner teeth gear 7 extends up to the outside of the system itself, by placing itself between two portions of the container 20 and therefore becoming a part actively suitable for enclosing therein the rest of the gears and planetaries of the system. In detail, in fact, the third planetary or inner teeth gear is constrained by means of a couple screw-bolt 22, 23 with a carter 41 in turn constrained to the tooth crown of the second planetary or inner teeth gear 10 that acts a geared wheel. On the opposite side, instead, the third planetary or inner teeth wheel 7 is constrained to a cover 40 that extends up to the holes from which the shafts la and 6a protrude from. Between the cover 40 and the third planetary or inner teeth wheel 7 there are further coupling screws 22, preferably radially arranged around the perimeter of the cover itself and oriented parallel to one of the axes X or Y.

In the embodiment shown in figures 4 and 5, a pulley 50 is fixed with contrasted introduction on said second shaft 6a. Clearly, said pulley shall not be intended as necessary for the development of the technical effects that the present system has.

Further blocking screws 31, guarantee the correct fixing between the pulley 50 and a terminal portion of said second shaft 6a, which rotates with respect to the cover 40 by the interposition of a bearing 30.

Into the second shaft 6a, observed that as in the previous embodiment, the first shaft la is always present, it is present a further bearing 13 that is shrunk-on therein and that presents a hole on its inner ring of a size such as to allow the passage of the first shaft la.

The embodiment shown in figure 4 further presents two bearings 13, 15 axially separated in correspondence of the first and second end. This advantageously allows to have an greater axial stabilization of the first shaft la.

The hereinafter table illustrates the data of the principal gears and inner crown wheels being part of the system object of the present invention.

Peripheral V 1.413 0.942 0.628 0.157 0.157

[m/s]

F [N] 10 20 10 40 40

From the aforementioned table it can be inferred that the transmission system with gear-box which is object of the present invention acts as a multiplier of torque on the output motion shafts and in detail on the secondary shaft.

Resuming, the system object of the present invention acts as a mechanism that operates on the variation of speed, that on one side transforms the reactive force in the active one, and on the other side increases the path traveled by the active force for 50%.

It is finally clear that to the object of the present invention adaptations, additions or variants obvious for a skilled person can be applied, without therefore departing from the scope of protection provided by the annexed claims.