ELLIPTICAL TRACKS

Description of the technique

There are not many alternative solutions to the gear differential, an attempt to make the ball differential was made by myself in the seventies of the last century.

The system involved the use of eccentric tracks with bearings, the invention was not successful, it as issued a patent on application No. 52910/70 A, patent number 9029531 based on the use of 2 eccentric tracks one inside the other.

The major car manufacturers discarded it due to the excessive cost of production as well as for the failure to solve some jamming problems and also for the excessive bulk on the diameter of the eccentrics in double overlap on two coplanar discs separated by a central cross. urrently these problems have been solved in an optimal way so we believe that the new Invention is valid to obtain the patent grant for Industrial Invention.

Description of the theoretical and practical principle of the invention

The differential derives from the observation that a cylinder cut at 45°, as is usually done when licing a salami, the cut shows an elliptical section useful to suggest that its peripheral ellipse can become a valid path to generate an intersection if it comes mirrored and superimposed. In fact, by replacing the cylinder with two tubes, one inserted into the other and cut at approximately 45°, the idea is that this path turns out to be an endless rotational drive of an intersection, in a rhythmic and progressive way. Figure 1 represents the above mentioned principle, if pipe (A) remains stationary and pipe

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SUBSTITUTE SHEETS (RULE 26) (B) rotates, the intersection is generated as in figure 2 where axis (H2) highlights the intersection point in which it is placed the symbol of a sphere (S). If tube (B) is rotated in one or the other direction, axis (H2) also moves to the right or to the left by dragging the cross point nd the sphere symbol with itself.

The symbol of the sphere also moves up or down.

In fact if the intersection was made with two tubes in which two hemispherical tracks were engraved, one for each tube with interposition of a pair of spheres, they would be able to drag in relative rotation any tube interposed between the two tubes. It is obvious to imagine the third tube with a double axial slot, longitudinal and opposed in parallel with the rotating axis of tubes (A) and (B).

In this way the spheres can rotate the central tube that we will call (C) by dragging it in relative rotation between (A) and (B), without the ends of tubes (A), (B) and (C) moving from the rotation plane. t should be noted that the intersections generated are two and opposite; in figure 2 the opposed intersection is not visible. Therefore a pair of tracks would move two spheres and vice versa the central tube will act simultaneously on two spheres; in figure 1 there is no intersection so you could not take advantage of the position that we would call neutral position or, dead center. In figure B two pairs of elliptical tracks per tube were drawn, the couples as a whole nsure that no dead center occurs together but that there is always an intersection to be exploited to obtain a towing relationship between pipes (A - B - C).

Looking at figure 3 we see that the inner tube (A), that could be a solid shaft, the central tube (C) on the left side develops with flange (C ') while the real tube contains shaft (A), in turn tube (C) is contained in tube (aB) which nds on the right with shaft (B).

Two tracks (al) and (a2) with concave profile suitable for the balls (S) are engraved in the tube (A), the two tracks are inclined and parallel. In the tube (aB) two other similar tracks are engraved but obtained in the inner side of the tube (aB) and they are not parallel but converging; track (bl) is exactly superimposed on track (al) while track (b2) generates a superimposed intersection ith track (a2); you can also see a sphere in the intersection (s2) and the groove (C ").

The sphere is 1/3 contained in track (A2), 1/3 contained in axial slot (C ") and 1/3 in track (b2)

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SUBSTITUTE SHEETS (RULE 26) of the pipe (aB). A crown (Co) can be applied to the flange (C ') of the tube (C), so by rotating the crown and tube (C) are dragged in rotation through the intersection (s2) engaged or with the ball and active tracks, both tube (A) and tube (aB).

The overlapping tracks on the left are neutral, but the two spheres are always engaged with the tube (C) so they enter the active towing phase as soon as one of the tubes (A) or (a B) slows down the rotation. Ultimately tubes (A) and (aB) can rotate through the crossings always in phase synchronized, or if one increases the rotation the other decreases it. Note that while the corner forms in the intersection on the left, on the right side the corner of the intersection disappears for superposition of (a2) with (b2).

The width of the corners at the maximum intersection reach maximum efficiency if they are built with the inclined slopes in the center with an inclination of 45 ° so that the intersection that takes over will always be 90°. lso in figure 3 intersection (a2) with (b2) must always be understood as two crossings for 2 spheres.

Figure 4 shows the tube (C) in which the slots (s2) containing the spheres are obtained, each two opposing slots need a pair of spheres, the slots are opposite and parallel.

DESCRIPTION OF THE INVENTION IN ITS APPLICATIONS s can be seen in the previous descriptive figures, any whole intersection made with an inclination of about 45°, develops with an excessive distance (E), measured length along the plane of the ellipse that joins two opposite generatrices of the shaft, see figure 2. So it can be seen that if the direction of the elliptical generatrix is reversed halfway, an equally valid path is formed from a mechanical point of view, but in a space reduced by approximately 50% (see figure

2.); but since, in fact, two progressive semi-ellipses are obtained,

(see ellipse V 'and the inversion line V and the rotation arrow v'), two crossings are created on the same polyline on each side for the application of two other spheres.

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SUBSTITUTE SHEETS (RULE 26) Basically there will be four active spheres for each pair of halved ellipses, which we would call semi ellipses. Figure 5 shows the principle where on the half circle (D) of the shaft 80. two inclined sections are made and in the middle section (ID) and (2D) two spheres plus two more can crossing on the opposite side or four spheres on the lines (1D - 2D - 3D - 4D).

But this system can be well used if tube (C) is eliminated.

In figures 5/6/7 and following the direction or sense of the elliptical generatrices are inverted with 85. some real curves like the guidelines (M-N) of 3/8.

As mentioned, the spheres should be rotated by the tube (C) which interposed between (a) and (a B), being tube (C) too bulky and difficult to assemble, a way has been found to replace it with a simpler system, which performs the same function of dragging the balls. It has been replaced by translators (T).

90. The solution of introducing translators has the advantage that tube (C) also disappears, as such, only the right part remains (see figure 3), that is a new shaft in line opposite to shaft (A), with the same external shape, in addition to this the spheres are engaged for ½ in the tracks and for ½ in the translators instead of 1/3-1/3-1/3 with great advantage for traction.

The two shafts (A) and (B) will be operational and driven by the spheres.

95. In fact, even real crossings disappear.

In theory, to make a cross the pipes must be superimposed while the system metamorphosed with translators, the intersection becomes only offset and virtual.

Figure 6 clearly highlights the trade-off where shafts (A) and (B) have become planetary shafts and no longer tubes, so they cannot be inserted one into the other too. but stay side by side and consecutive on the same construction axis.

The tracks of (A) al and (B) bl are parallel to each other.

The track (a2) of the shaft (A) and the track (b2) of (B) are converging or mirrored.

If (b2) were superimposed on (a2) it would generate a crossing with (a2) of (A); moreover both track (a2) and track (b2) as well as being convergent are rotated radially by 45 ° with respect to 105. tracks (al) and (bl).

In figure 6, a dashed track has been drawn over track (a2) as a symbol that reproduces track (b2), which is really on the right, so the intersection is in the two distinct shafts only virtual, as already mentioned, and does not exist in reality.

In order to obtain it, it is sufficient to introduce the translator (T).

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SUBSTITUTE SHEETS (RULE 26) no. In figure 7 are shown the same shafts (A) and (B) opposed and approached to the center with dash and dot, so as to contrast each other and maintain the same rotation plane common; even at the ends of the shafts the containment plane is created, as it is seen from the hatching at the two ends of (A) and (B).

In the center of (a2) and (b2) of figure 8 there is the symbol of two spheres, which are 115. inserted half into the translator (T) and half into the tracks (a2) and (b2).

To better describe the semi-ellipses, figures are used as if the ellipses were not-folded in the middle but seen as in figure 2', with the arrow (V) that represents them in figures 9 - 9c - 9d. The ellipses that intersect in the various figures are also represented as belonging to the two shafts in transparent view along the axis of rotation on a plane.

120. Figure 9 represents the theoretical problem and the solution that derives from the use of the semi-elliptical slopes with four spheres for each couple in two spheres for each couple.

In the figure we see 8 spheres, 4 for the tracks (Z) and 4 for the tracks (R), (zeta and erre are the names) necessary to better describe the invention which is explained below.

The track (Z) in bold develops for half a circumference to the right and left, then it converges 125. and goe back; by right and left is meant as in the figure (5), detail (P); in figure 9 You can see the ellipse (Z) and the symbol of four spheres si - s2 - s3 - s4.

It must be imagined that the tracks are two overlapping ie in neutral position, the bold ellipses indicate two overlapping tracks or one is of the shaft (A) and the other of the shaft (B), they are projected on the same rotation axis; this position is the dead point in wich 130. there is no crossing, so there is no towing in sl-s2-s3-s4 .

Instead tracks (R) are crossed and can pull shafts (A) and (B) as one belongs to shaft (A) and one belongs to shaft (B). It should be remembered that the intersection is virtual as in figure 8 between translator (T), (a2) of (A) and (b2) of (B).

If we observe the line that forms the central cross (CR ') with the horizontal axis we can see that 135. the intersection of the tracks (R) and the respective spheres are in line with the spheres (si - s2 - s3 - s4) of the tracks (Z), so that an incompatible orthogonal system is generated, which is explained later. Four spheres are superimposed on the other four and since all spheres must be held and controlled by the translators which cannot be superimposed as are around the circle; it is represented in figure 10 in which you can see only n. 4 140. translators (T) partially inserted in the tube (Cl) with the relative spheres, see perspective of

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SUBSTITUTE SHEETS (RULE 26) translator with two balls, one of which will be constrained halfway on the shaft (A) and the other will be constrained half on the shaft (B).

The spheres on the horizontal line belong to the tracks (R), (r6) and (r8), the spheres in vertical to the slopes (Z) or (si) and (s3). In figure 9 the spheres (s2) and (s4) of the tracks (Z) have been eliminated (E), and from tracks (R) the spheres (r5) and (r7) have been eliminated (E).

To better describe the rest of the invention, it is clarified that the term spheres must also be understood as rollers and vice versa.

In figure 8 the translator is drawn and symbolized also sectioned (T ') and (T); in this case (T ') belongs to tracks (Z) which are always parallel and the translator (T) belongs to tracks (R) which are always converging in the center and rotated.

As you can guess, if one of the shafts (A) or (B) rotates in the opposite way to the other shaft, it happens that the spheres already constrained by the translator keep the invariable position in length, i.e. well spaced - see distance (L) between the arrows - the spheres would allow such rotation being half-encased in their respective tracks, provided that the translator follow the rotation in one or the other direction and move to the new position longitudinally.

Note that the four translators are constrained by the tube (Cl) and slide in their seat longitudinal. Ultimately you get the same effect that occurred with the crossing in the figure 3, in which a single sphere participates 1/3 in the tube (A), 1/3 in the tube (C), 1/3 in the tube (aB), in the intersection it is evident that the tube (C) drives in rotation both the tube (A) and the tube (aB) and at the same time allows the free deceleration of one of the two and consequently the acceleration of the other, always on condition that a valid intersection is used between the tracks of (A) and (B). he difference between the two examples lies in the fact that the differential effect in figure 3 is obtained between the slot of the tube (C) and the two overlapping tracks, using the track (b2) e (a2) with a single sphere, while in the example of figure 8, the differential effect is obtained using two spheres, bound to the tracks (a2) of shaft (A) and (b2) of shaft (B) of the translator (T), which as already mentioned replaces the tube (C) or in the slots (s2) of the ube, see figure 4.

The great advantage of the translator system is that the right half shaft tube (aB) in figure 3, leaves the overlap space to the translators (T) and the translators (T) are incorporated in the Cylinder (Cl)

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SUBSTITUTE SHEETS (RULE 26) in figure 10, which contains the whole as SPHERES OR ROLLERS DIFFERENTIAL MOTION ON CONVERGENT SEMIELIPTIC TRACKS). Figure (10) of 1/8 shows the cylinder (Cl) in which the four seats can be seen as semicircular (Se) and the four translators (T) and a translator with two spheres inserted in its seat in perspective, see perspective figure, superimposed.

The detail (Cl) presents the set of 4 translators (T) partially embedded in the cylinder (Cl) engaged as per derivation expressed in figure (9) or (r8) with (r6) and (si) with (s3) in figure 10. he previous observations allow the realization of differentials whose characteristics and relative advantages will become clearer through the indicative and therefore non-limiting description of its preferred embodiments as represented in 2/8 where a schematic embodiment of a bridge differential is shown.

In 3/8 a second embodiment is presented as in the following tables a third shape and ome variants of the differential in its industrial applications are represented.

Figure 11 of 2/8 , shows an assembly (11) consisting of a sectional casing (8) or one traditional non binding differential box, inside which you can see shaft (A) opposed to shaft (B), contained by the cylinder (Cl) on which there are two ways of Crown assembly (Co) that are non-binding but only descriptive systems of economy of costruction; t the top it can be seen that the cylinder is closed by a flange (F) such as cylinder cap (Cl) screwed by thread (F "), above the flange (F) the crown gripping the morse cone (Cm) is conified, at the head of the cylinder (Cl).

In the lower part (0s) you can see the screwing and locking with bolts.

It should be noted immediately that in the system below (sO) the flange is largerand more expensive lso for the use of bolts; the advantage of the possibility of disassembly does not justify the greater cost.

In addition to the differential set, you can clearly see the shape and proportion that the details have. The translators (T) drag two spheres each, the two concave tracks are built on each shaft for medium-sized spheres. The short translator (Tc) is drawn at the bottom left and in the center the translator elongated (T) is drawn that is the translator is not symmetrical but on the one hand it is longer; the reason for this elongation is that the translators are assembled tangent to each other and they together form the tube containing shafts (A) and (B), see also figure section 10.

This way of containing shafts (A) and (B) is beyond valid and tenacious in system with

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SUBSTITUTE SHEETS (RULE 26) four translators, whereby their elongation guarantees a better mechanical resistance to torsion, in translators (T) the spheres are also represented.

Figure 12 shows how economical is the construction of the translators designed for the invention; they are obtained from a round drawn steel section.

The profile is already made to measure with a longitudinal cut drilled at the same time with milling, see tool (U), figure IB, that represents a progressive and variable shape of the core in the cross section of shafts (A) and (B).

In figure (10") you can see both spheres and different rollers, on the left it is highlighted as one sphere in the segment (TA) does not undergo tangent contact since the segment (TA) is a line traight, necessary to insert the sphere from underneath at the end of its stroke with the hole recirculation (F) in the cradle (cu), see figure (11T).

This stroke (TA) is well used if you replace the sphere with a threaded roller from above, which can also be partially conical in order to obtain a correct rotation as well as a more tenacious grip with the semi-elliptical tracks of the shafts, obtained close to each other; on the left is a train of spheres useful to reduce the friction between the translators, completely optional and not binding.

In figure (11C) and (31) of 2/8 there is a cylinder with interlocking teeth, and a union ring (ac) or a central section of 2 half cylinders (Cl) in a descriptive and non-descriptive way limitative in which 4 negative teeth (QC) are drawn and ruled into which the 4 are fitted arms of the cross (CR) if the cross is built with long arms, being installed in the center, unites the two half cylinders in a single piece which contains the shafts and translators, it must be said that the cross in practice performs the function of other translators but only for the elliptical tracks obtained on the front of the two shafts (A) and (B), in figure (11C) a cross with 4 arms is schematized (QC ') and with four grooves (SC) in which 4 spheres dedicated to the vertical elliptical tracks (VR) and (VZ) of the shafts, referred to in 7/8. The differential can be obtained by miniaturization without losing the applied power in a similar differential with only two races per shaft and with very spheres or rollers.

This type of differential is indispensable when you have space in length and not on diameter.

The practical application is represented by the new electric traction technologies for electric cars, in them the same engine could contain the differential as a shaft rotating, and becoming an electro-differential shaft; 3/8 presents this application as an improvement for the electromechanics of this technological sector;

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SUBSTITUTE SHEETS (RULE 26) another application could be represented by use in truck vehicles.

Figure 14 represents the differential which we will call for convenience long differential, in it the shafts (A) and (B) are very elongated and the tracks are repetitive nd the same type by type to be adequate to the torque to be transmitted.

In shaft (A) 5 tracks are engraved which we will call zero (Z) and also five other tracks which we will call rotated tracks (R), the number of tracks are explanatory and not limiting.

In particular, it should be noted that the aim of the following invention is to reduce the external diameter of the differential by more than 50% with the same torque ransmitted by a differential traditional gear.

To achieve this, I made the invention without the gears of planetariums and satellites obtaining a cheaper and lower industrial product use of steel. This allows the invention to be used as a rotating shaft of an engine electric in use for the automotive industry, the shaft is already differentiated on both sides of the rotor whose overall dimensions do not increase the diameter f the supporting structure or the size of the windings or magnets.

The other advantage is obtained in the industrial production process entirely delegated to numerically controlled lathe; this produces a saving of 85% on the cost of skilled labor, generating a constant economy of scale particularly relevant in the differential called "elonged" well highlighted in 3/8 ith figures 14-15 and in the figures 32-33-34-35-36-37 of 8/8.

As in the two system tracks per shaft, even in the system that we define as a track system multiple side by side, it should be noted that the 45 ° radial rotation of the incision of the piste (R) is obtained in both systems in the same way.

In the figures the tracks (Z) and the tracks (R) ook different but they are just positioned differently so that tracks (Z) and tracks (R) are identical, their name derives only from the different engraving position.

The container tube (Cl) at its ends (EC) is closed with the screwed ferrules and conified by the cylinder, in this way shafts (A and B) remain constrained by the rotation planes and in perfect hermetic operation, see also 5/8. /8 represents the CAD of the shaft - type - with four tracks (Z) plus four tracks (R) and also the two opposing shafts whose tracks are proportionate to related spheres.

In 3/8 at the top left are drawn the 5 trace lines of the "centrosphere Z" tracks, as theorized, by wrapping the lines on the shaft the semi-ellipticals and converging formations are generated,

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SUBSTITUTE SHEETS (RULE 26) he terminal (M) joins with the terminal (N). The group of lines belonging to each tree of the type R was drawn higher than half a curve, which indicates that once the construction of the track group (Z) has been completed, there is a shaft rotation of 45 ° before starting the incision of the slopes (R).

With this concept as a whole, the spheres can occupy precisely the cross circular formation 90 ° + 90 ° that you can see in tyable 1, figure 10, and in 7/8 figure 27 in 6/8 figure 19, in 2/8 figure 11, in 3/8 figures 14-15, 5/8 figure 18.

If we wanted to use eight translators, the rotation of the tracks (R) would be 90 °, we will call this type of track (R90 °) to distinguish it from the tracks named (R) which allows the use of double the spheres, in this case the spheres are found to take over not a 90 ° but at half stroke or 45 °, so in the continuation of the differential towing a balanced intersection takes over where the zero point moves and rises towards 22.5 ° while the 45 ° group moves and falls towards 22.5 °, the "zero" point means the neutral point, that is an instant of the rotation. Although this choice is active with 4 + 4 balls per shaft, it is less sensitive than the 4 system translators, where the zero point moves and rises towards 45 ° meets with the other group that moves and descends from 90 ° to 45 °, that is to say that the system with four translators, although use only 2 + 2 spheres at each change of towing it is perfectly well balanced, always with the minimum grip at 45 ° and maximum 90 ° on 4 spheres. he set of tracks (Z) and tracks (R) can also be created alternately, in this way we get a better resistance of the trees to torsion for which we would have, for each tree the arrangement highlighted in the figure 15 of 3/8, from left to right starts the track (Z) and then track (R), then (Z) and then (R) so on, and ending with the opposite track to the first. Figure 15 also highlights the following, both the tracks (Z) and the tracks (R) come engraved in the shafts (A) and (B) with a lesser depth, even half as much occurs for a normal differential with 4 rollers or spheres as shown in figure 11.

The reason is that in the long differential we use multiple tracks; the sum of the Thrusts of the rollers or spheres will give the pulling power, a bit like it happens on a screw with ball recirculation, in this case the translators are assigned a grip more than double compared to the depth of the semi elliptical tracks on the shafts.

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SUBSTITUTE SHEETS (RULE 26) In figure 15 we see the line (a) which represents the depth of both the tracks (Z) that of the tracks (R), while above it can be seen that the depth of the gripping hole (b) on the translator (T) is much greater, but still to be evaluated.

The low depth of the tracks engraved on the shafts (A) and (B) is the great advantage that allows the core of the shafts (A) and (B), to become robust on very small axes in diameter, in which the minimum depth of the tracks does not decrease the power transported, since the number of tracks is the multiplication factor that the designer will use in order to calculate the total torque required.

If the cylinder container should be the base of the magnets or vice versa of the coils on an electric motor it will be faceted (SF) as seen from the section on the bottom left, see in 3/8.

Figure (11T) 2/8 highlights the particular precision of the hole (Fr) called "hole of pressure and recirculation" of the translators, which allows the spheres to discharge the axial centrifugal thrust derived from the resistance of the shafts. This thrust would be discharged in the rotation cradle (Cu) around the guide seat of the spheres in the translators, therefore with this expedient to the translators is subtracted the containment pressure of the spheres, which partly passes through the hole (Fr) of the translators (T) and discharges onto the cylinder since the internal measures intended for the spheres of the translators are calibrated in order to tangere without deforming. In conclusion, the translators have the task of guaranteeing and calibrating the exact distance between the two spheres or four spheres or six spheres and so on without undergoing the total sticking effect due to excessive pressure which we will call center- block pressure between translators and the sliding seats (Se) of the cylinder; it is obvious that this block center pressure is totally eliminated (E) using cylindrical rollers or low taper rollers, see example figure rollers and spheres (10 ") in 2/8.

Figure 16 in 3/8 represents a cylinder with eight translators that use double of the rollers or spheres with respect to the system with four translators, already described. The numbers 1-3-5-7 indicate the rollers on tracks (Z) and the numbers 2-4-6-8 indicate the rollers on tracks (R), better highlighted both on the right and on the left of the figure 16.

On the right the symbol of the reels for the tracks (Z) has been highlighted, on the left the symbol of rollers for the tracks (R), so if the tracks on the right are in neutral zero position (Z), and the active tracks (R) on the left, as you can imagine, the active tracks are positioned with the

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SUBSTITUTE SHEETS (RULE 26) spheres or rollers at 45 ° interposed with the tracks (Z): it happens that the intersection of minimum traction will occur at about 22.5 ° as evidenced by the two opposite arrows at the top right, please note it is a crossing with eight spheres or rollers. (See figure 9D).

In fact, the tracks (Z) from the neutral position (O) begin to form an intersection and towards 22.5 ° they balance with the intersection, active which was at 45 ° and descends towards 22.5 ° to disappear at intersection (O), while the increasing intersection leads back to an ever increasing intersection active towards 45 ° and more up to the maximum crossing 90 °.

In figure 9d in 1/8 the point of minimum and balanced traction formed is better seen from eight spheres of which four spheres at about 22.5 ° on the vertical ellipse at the top and bottom, and the another four in an average position inside closer to the center, all active; figure 9c shows the eight translators system again which is realized as already said by engraving the track (b2), rotated 90 ° with respect to the track (a2), while the track (a2) must be in the same position of the runway (al).

This means that if (al) and (a2) are equal, that is in shaft (A) it is sufficient to engrave a single track which performs a double function, therefore (al) can form the crossings not only with (bl) but also with (b2), defined in the example (Rb2), the confirmation can be seen with figure 17 in which the runway (Rb2) seems mirrored by the runway (Zal) and the runway (Bl).

We will call this track (Rb2) considering the vertical ellipse as track (Zal) figure (9d), the horizontal track as track (Rb2) figure 9c, you can see that the intersection is generated rotated by 45 ° with respect to the tracks (Z) in the neutral position at the intersection of figure 9c.

While the four spheres are positioned interposed, in the cross that we have symbolized with four squares, in practice there are eight positions for eight spheres, therefore eight translators perfectly equidistant every 45 ° with the symbol of squares and spheres. Their operation is just as balanced as the four out of four shifters system spheres but only more powerful. But not only that, one of the trees as it uses a track for two functions, such a shaft can be shorter than 50%, in this case the advantage is evident in the realize the differential called short, instead of four tracks we would have three tracks, one for the shaft (A) and two for the shaft (B) or vice versa in figure 17 in 4/8 shows the differential with three tracks that we will call (short shorter) in which there are 5 lines

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SUBSTITUTE SHEETS (RULE 26) horizontals that join the sphere centers two by two, which indicate the grip of the relative ones translators, the lines are the symbol of the translators on sight so as not to complicate the figure, three lines are not seen being behind, not in sight.

In the differential that we will call long we want to achieve the miniaturization so we will use only four translators that occupy the entire circumference on a diameter very small so you will not have this opportunity of 8 translators.

In figure 14 and in figure 15 it has been shown that the translators (T) are always shorter of the container tubes (Cl) as much as is the translation stroke of the semi-elliptical tracks, stroke highlighted by the arrows (FT). In the most sophisticated differentials where sliding friction is excessive it can be avoided creating four junction lines (Q ") that join the cylindrical curved seats for which it is possible to interpose a train of spheres (S) that separate the translators, on which it comes obtained the concave seat as in the bearings, the arrangement is equally valid a counteract the thrust center block while improving the smoothness of the ranslators (T) in which the sliding friction is transformed into rolling.

The figure (11T) and (10 ") shows the section of the translators (T) with slots for bearings and spheres (s). 5/8 shows again the differential for miniaturization with multiple tracks, the which guarantees a great pulling power no less than the differential with large spheres on four translators in four semi elliptical tracks. s already mentioned, the goal is to use minimum shaft diameters without losing value of torque transmission. 5/8 at the top left of the figure (18a) shows the section of the cylinder with four translators in which four spheres guarantee the perfect use of four translators. As can be seen in the figure (18a) the four spheres pass through the translators (T) and engage with the guide track grooves in the cylinder, this means that the ylinder drags the balls (S) without the mediation of translators (T) for the rotary pulling thrust in this way the spherical masses (S) drag shafts without generating the thrusts that we have defined as center of block on the translators.

The shifters have only the task of keeping the gauge for the intersection of semi-elliptical tracks converging, in this way the translators are totally hooked to the spheres without suffering ven minimal bonding forces, even in the rotary thrust phase. But for the better specialize the invention and in the face of any deformations that would be generated in the arc of the tracks dedicated to the spheres, we have also kept the tracks for the translators, with this a

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SUBSTITUTE SHEETS (RULE 26) perfect symmetry is generated, each track for spheres is located within the largest track or the track of the translators. he figure (18b) shows the centers of the four tracks for the spheres thus numbered

1 - 2 - 3 - 4 and the center of the tracks for translators (T) with n. 5 - 6 - 7 - 8, as you can see each track for sphere is in the center of another track for translators. The four points of the star in the center represent the meeting of the four tracks of the translators (T).

Figure 18 is partially sectioned mixed in which it is highlighted that the tree (A) hermetically closes the cylinder with round gasket (y) of non-limiting shape but only descriptive, in order to contain the lubricant inside the cylinder, on the left we highlight the mechanical closure with screwed and crimped counter-thrust ring nut on anti-unscrewing pressure cradle. In figure 17 the ring nut is different and unique and is screwed in the circumference outside the cylinder. Also in the figures in 8/8 the ferrules are screwed into the outer circumference of the cylinder (Cl).

The system guarantees the invention for a long life without maintenance, not limiting but with an objective guarantee.

Between the shaft (A) and the shaft (B) in the center a series of spheres are assembled to create the counter thrust bearing (Yc); visible also in figure 18a, this arrangement s useful to make the differential perfectly self-centering as well as more sensitive.

The bearing balls (Yc) are also installed between the nuts (EC) and the shafts, the bearing race can be seen clearly in the screw nut (EC) at the bottom 5/8, the same seat can be seen in the shaft (B) in which you can also see the contrasting spheres in the center.

As you can see, the central translator (T) is dedicated to the six spheres of the tracks (R). bove the sectioned translator is dedicated to the tracks (Z) in which it is highlighted that the sphere (s) is inserted from above, see arrow.

On the left you can see the section of the translator (T) and also the sphere (s) that is positioned from the top to the center of the translator in order to serve the three elements: the cylinder (Cl), the shifter (T) and shafts (A) and (B). n the center on the right you can see the shaft (B) which indicates the position for the gasket hermetic (Y), below is the cylinder (Cl) with sectioned ring nut, it is obvious that the cradle deformation (x) occurs after screwing the ring nut (EC).

As you can see, the essential part of the differential consists of a few elements, namely: cylinder, translators, balls, shafts, ring nuts and gaskets and any locking solenoid (SBL), of which

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SUBSTITUTE SHEETS (RULE 26) ach detail allows various characterizing applications.

6/8 shows the differential lock with the particular solenoid shaft (SBL), it is in the center between the two trees (A) and (B).

The left part of the detail finds the shaft (A) drilled that accommodates the side (1), on the right side the terminal (E) is inserted on the shaft (B). n figure 19 the detail (E) is inserted inside the shaft (B) which offers the hexagonal shape of the grip. The hexagonal part of the solenoid, sliding to the left, fits into the seat of the same shape (F) in the shaft (A) so that one part of the hexagon always remains in the right guide on (B) and the other part sliding on the left it engages the shaft (A).

In this way the two shafts become a single shaft and the differential moves n unison, at the center of the shafts, on the left, four rows of coil are drawn at the top of the fixed casing (8) to indicate the electric circuit of a solenoid which generates an attractive magnetic field when the electric current passes pulls the anchor (FM) of the solenoid shaft (SBS) to the left, to join the two shafts (A) and (B) in a single shaft; the contrast spring (M) brings everything back to rest with the opening of the electrical circuit. lways at the top, with the inclined dashes it is meant that, as in the Brushless gear, magnets are integral not only with the rotor also in the facets (SF) with the differential cylinder which we have defined as an electro differential spheres shaft.

The flat lines symbolize the stator integral with the cover on which it is seen the thrust bearings and the caliber rollers for shaft A, stator and otor which can also be reversed.

The whole is designed as descriptive and non-limiting reference points of the invention.

Figure 20 shows the magnetic iron terminal (FM) as an anchor, screwed into the stem (1) of the solenoid (SBL).

Figure 21 presents a pneumatically operated solenoid of shape and grooves for the elative rubber pads, and the air passage (Ap) on the crankcase.

Finally in figure 22 an application is highlighted in a descriptive and non-limiting way ultra-defined sphere, so it can always be well calibrated of any diameter; in this calibration it is possible to distribute the guide curves in the two tangent points grip in the cylinder and the curves obtained in the drive shafts. he figure shows the figure and thrust direction, which is placed on a ortogonal building

15

SUBSTITUTE SHEETS (RULE 26) where all forces coincide with the center of the sphere (S) and all components are parallel, PI and P2.

In this type of ultra definition the translators T are not guided in the longitudinal tracks of the cylinder but are guided by the spheres and are built concentric to the shafts (A-B) and ylinder (Cl) and have a uniform thickness such as to fill the gap between shafts and cylinder.

In 7/8, figure 27 represents the short differential with large spheres, which uses shafts A and B of the same size, with a single track obtained in the circumferences, see figure 24.

In the circumferences of the shafts (A) and (B) the tracks are of type Z parallel to each other, this means that the position as drawn does not generate intersections and therefore there is no towing, the intersection is obtained by engraving the elliptical tracks for the intersection on the front of the shafts (A) and (B), for which the towing must be generated by the elliptical tracks obtained on the opposing convex fronts of the shafts, and, as seen on the left of the central figure, the whole ellipse (EC) is obtained horizontally, while on the right it is obtained vertically, and the intersection will form exactly at 45 ° that is they are four crossings with four spheres, as in figure 28.

In the central figure 24 of the shafts you can see the opposed rounded planes (BO) in which two spheres (S) of the four that generate the intersection are drawn as mentioned above better highlighted in figure number 28, the four spheres are positioned at the center of the intersections between the two raceways (VR) of the shaft (A) and (Vz) of the shaft (B). In figure 26 we see the cross translator cut into two parts with its four slots (SC), in the cross two arms (Qc) on the left are drawn longer but only in an alternative way and not limiting as they could be even shorter (Q ') if the cylinder were whole. Also in figure 30 it can be seen that if the 4 arms of the cross were the same and long, they would fit into the joints (Qc) of figure 30 and the cylinder would be obtained in two parts hile the arms would be short (Q '). If the cylinder were made in a single piece, these arms would find the joints in the tracks (Q) of the long and entire cylinder formed in a single piece, see visible joints in figure 30.

The four central spheres (Sr) figure 29 slide in the grooves and are simultaneously constrained in the vertical elliptical track (VR) of the shaft (A) and (VZ) of the shaft (B) tracks ighlighted as in figure 24 and in the slots (Sc).

In figure 23 the same cross translator is also seen in vertical section with equal arms.

16

SUBSTITUTE SHEETS (RULE 26) The cross (CR) occupies the space between the two shafts (A) and (B), but is constrained to the cylinder (Cl) in a stable way or in the joints (QC) of the cylinder or in the raceways (Q). At the center of the shafts it freewheel and concentric with the axis (H) of the shaft (CC). n figure 29 all four points (QC) of constraint with the cylinder are shown in a descriptive and non-limiting mode, and the four spheres (SR) are visible in the tow phase, between the cross central (CR) in the elliptical tracks (EC) called (VR) for the shaft (A) and (VZ) for the shaft (B).

In the central figure 24 only two symbolically smaller spheres are drawn for better represent the gripping position between (A) and (B) interposed on the central (CR) between the track (VR) f (A) and (VZ) of (B).

Figure 25 represents the lateral approach of two translators (T) and between one and the other the terminal part (QC) of the cross which passes into the exhaust on the sides of the translators (T), to be constrained in the cylinder (Cl), the two arrows (F) indicate the direction of movement of the translators (T), while the terminal (QC) of the cross remains fixed on (Cl); as you can see theentral part of the translators (T) is unloaded to allow the passage and attachment of the cross to the cylinder with its arms.

In figure 30 we see the cylinder (Cl) which can also be half a cylinder with the center-axis of the tracks (S) for the spheres and the center-axis for the translators (T) and the center-axis of the guide tracks (Q) and the latter can only be obtained up to half the length of the cylinder (Cl). he rounded parts (BO), also called ciambellate, in a descriptive and non-limiting way, of the shafts (A) and (B) allow the better use of the spheres for towing between the cross translator which is also convex at points (B), figure 23-24, the convexity (B) finds space in the concavities of the tracks (VR) and (VZ) of the convex shafts (A) and (B), similarly the ringed walls of the shafts (A) and (B) determine the variable thickness of the mating cross. As you can see, this system of obtaining the elliptical tracks in the two opposite fronts of the shafts (A) and (B), where (VR) is rotated 90 ° relative to (VZ), is the same as in the eight system translators in which the tracks (R) are rotated by 90 ° with respect to the tracks (Z), so in the tracks (Z) of the circumferences four spheres are applied to each track of (A) and (B), the tracks are parallel to each other. Two spheres in the central figure 24 are not visible. he fact of having the tracks (VZ) and (VR) opposite each other avoids having eight balls in one single shaft track (A) as in 4/8 and at the same time allows the differential to be made with shafts equal in length.

17

SUBSTITUTE SHEETS (RULE 26) The system is more compact and equally well balanced but cheaper, being of further reduced dimensions. It should be noted that the elliptical tracks on the opposite fronts of the trees can overflow the circumference at points (E), as the overlapping of the tracks in those points does not generate traction but only synchronism between balls and cross (CR).

This way of obtaining the elliptical tracks (EC) in order to have two tracks synchronized with the translator, central cross and the other two tracks in the circumferences of the shafts (A) and (B),ynchronized with the four translators (T), allows the mixed use of spheres in the center between the shafts (A) and (B), and of rollers in the elliptical tracks of the circumferences, in particular of rollers of the flared type as presented in the translator (T) of the figure (10 ") in 2/8. Note that if the entire cylinder is made up of two half cylinders as shown in the diagram 31 in 2/8, the positive teeth (B) belong to the half cylinder (Cib) while the negative nes belong to the half cylinder (Cia) and the elastic ring (Ac) fits between the two half cylinders and the cross in the recess (C) of the three details. Everything is presented in a non-limiting but only descriptive way.

To better define the differential with elliptical tracks in 1/8 it was noted that each pair of ellipses forms number 4 crossings and the pairs of ellipses are 2, i.e. the differential to be able to ork must have at least two pairs of ellipses per shaft, in which the crossings are 8 and since the diameter of the differential must be as small as possible the smallest differential with four translators has occurred.

As noted in the theoretical figure 9 we used two spheres on two crossings of the first pair and two other spheres on the other two crossings of the second pair as in figure 10; n fact a total of four crossings of the four-shift differential were not used.

So only in the description of the 8-shift differential we used the crossings available with two pairs of ellipses and a more economical way to obtain a type of 8-shift differential was transformed. Then in the construction of the differential with three elliptical tracks it was explained that in the shaft (A) uses a single elliptical track (Z) with respect to the differential of figure 11, nd in shaft (B) it uses two elliptical tracks, one of the type (Z) and the other of the type (R), since the shaft (A) is as if with its single track (Z) forms all the intersections, 4 of which with the track (Z) of the shaft (B) and 4 with the track (R90) always of the shaft (B).

Therefore we have translators that engage 8 spheres on (A) and 8 spheres on (B) of which four

18

SUBSTITUTE SHEETS (RULE 26) of the shaft (B) in the track (Z) and four in the track (R).

This has meant that eight translators around a circle are placed side by side every 45 °, and every shifter works in pairs with the other opposite shifter on the other side of the diameter of the circle on which it is installed and moves in the same direction in unison with its twin.

Now the following should be observed: if in shaft (A) we use both tracks, we could do it nd couple the track (R 45 °) with a track (Z) of the shaft (B), this is possible in how much in this differential the track (R) of (B) is rotated by 90°, as explained in system a 8 translators, for which the track of (A) (R 45°) must be coupled with the track (Z) of (B) which has only four balls. The track is in fact engraved with a radial rotation of 45 ° and creates the intersection placed at 22.5° or our intersections at 22.5 ° with the track (Z) of (B) on one side only, see arrows (F ') in figure 9. Therefore we would have the track (R) of the shaft (A) coupled with the track (Z) of (B) and the translators will be 12 translators, i.e. the number of balls increases the transmitted torque.

In conclusion, the differential theoretically forms many crossing points, all of which can be exploited with the translator system, each of which can be dedicated to an intersection formed by the ellipticalracks made in the circumferences of the shafts (A) and (B).

In these cases the spheres increase and they can be smaller and smaller as explained in the differential for miniaturization and carry the right torque. It can be shown that the increase in the number of translators can be inversely proportional to the size of the diameter of the spheres, with the same Torque transmitted. he differential will have 12 translators, and in the track (Z) of the shaft (A) it will have 8 spheres like the differential with 8 translators and 4 spheres in the track (R45 °), while in the shaft (B) it will have 8 spheres in the tracks (Z), 4 more than the 8-shift differential and 4 spheres in the tracks (R90 °) and the shafts (A) and (B) will be equal in length.

This principle of the track (R 90 °) on the shaft (B) can further expand to 16 translators, ne every 22.5°, in which the track (R 45 °) of (A) is also coupled with the track (R90 °) of (B), completing the alternative taps available, so the 16-shift differential will work as a powerful differential towed by 32 spheres, or 16 for the shaft (A) and 16 for the shaft (B). PLEASE NOTE in 1/9 figure 9 describes the use of 4 translators; in the same scheme of figure 9, we introduced 4 arrows (F ') which represent the meeting of the tracks (R 45 °) of (A) with the tracks (Z) of (B), in which (F ') represents the real intersection at 22.5°,

19

SUBSTITUTE SHEETS (RULE 26) but if we want to see the intersection also in the 90 ° track of (B) we introduce the example with the figure (9E) only in order not to complicate the figure 9, in which the intersection completes by another 22.5 ° the perfect equilibrium of the circumference.

The four arrows (F ') and the four triangles (tri) in figure 9E show the perfect balance of 16 points described as conceived in the semi-elliptical system also known as bent elliptical tracks.

By a practical point of view it should be noted that the translators must always be in couple to maintain the perfect balance of rotation and must be minimum 4 and increase rogressively from 4 to 8 and so on.

Figure 9E also highlights how each pair of spheres generates connecting axes that meet at the center with the axis of the other spheres whose projection is always 90 ° in the center. (See triangles and arrows of figure 9E better highlighted).

Figure (9E) can be better interpreted if we consider that: both the arrows (F ') and riangles (tri) represent eight crossings, or eight translators.

While figure (9c) with the four square symbols and four round symbols represents eight other crossings, or eight other translators.

Observing and superimposing the two figures we see that the symbols of figure (9c) occupy the points each 45° intervals on a circumference, while the symbols of figure (9E) occupy the midpoints of 22.5° etween the 45 ° intervals of figure (9c) of sixteen translators, which will be perfectly coupled in an entire circumference to the 16 spheres of (B). And it must be imagined that every instant of the rotation ZERO = Z disengages four spheres of (A) and four spheres of (B), it follows that in this coupling we would always have 32-8 = 24 spheres active for rotation, that is we would have 12 spheres for each tree. ith the same reasoning we can affirm that with a differential of four translators we would always have in traction a minimum of two spheres per shaft.

This reasoning holds true only when we analyze the two-lane differential for each shaft, but if we face the analysis of miniaturization where the theory of long shafts with four translators of active spheres for traction will be as many as there are he repetitions.

In the example of the shaft with four tracks (Z) and four tracks (R) per shaft we will always have 8 spheres per shaft active for rotation in the instant ZERO, and 16 in the rest of shaft traction.

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SUBSTITUTE SHEETS (RULE 26) The differential object will be limited only by the dimensions that the designer will use to representhe invention in the most useful way for his project.

In figure of 8/8 the object of claim 1 is presented of which from figure 32 to figure 36 a form of differential can be distinguished in its essence, i.e. shafts (A) and (B) of figure 32 are separated by the opposite spheres in the center and at the ends where they meet the caps or ring nuts (EC) of the cylinder (Cl). Figure 33 highlights he assembly of the four translators (T) with the spheres (S) in the shafts (A) and (B), figure 34 shows the assembly of the cylinder in cut form with spheres and ring nut (EC) screwed into the outer circumference of the cylinder (Cl) inside which you can see the shafts and translators. Figure 34 represents the main figure in its form of applicability in the automotive industry. Figure 35 presents the 4 translators in part eparated from the assembly, figure 36 shows the cylinder (Cl) in which the internal sliding tracks of both translators (T) and spheres (S) can be seen, figure 37 has two long shafts (A) and (B) of the type with multiple tracks, this figure represents an example with four tracks (Z) and four tracks (R) for each shaft (A) and (B), used for the realization of a form of the differential called differential ong or miniature dedicated in particular as a differentiated shaft for electric motors, also useful for being installed in the gearbox of a traditional engine and also useful as a differential to be installed on the deck of trucks of any capacity.

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SUBSTITUTE SHEETS (RULE 26)