ITRM20110537A1 - HYPOCYCLOIDAL SYSTEM BICUSPIDE FOR THE CONVERSION OF THE MOTORCYCLE BETWEEN ALTERNATIVE AND CIRCULAR LINES - Google Patents

Description

DESCRIPTION OF THE BICUSPID HYPOCYCLOIDAL SYSTEM FOR THE CONVERSION OF THE MOTORCYCLE BETWEEN ALTERNATIVE STRAIGHT AND

CIRCULAR

The present invention relates to an innovative crankshaft in which the ordinary connecting rod-crank mechanism does not develop directly between two half-shafts and the big end but indirectly thanks to the interposition, between the crank pin of each half-shaft and the big end. , of a further rotating organ (hereinafter defined for convenience simply as 'intermediate organ', if in the singular, and 'intermediate organs', if in the plural and, in any case, without apices) and made in such a way as to allow the connecting rod head to move with reciprocating rectilinear motion, which allows the connecting rod to be replaced with a slider rigidly fixed and coaxially to the piston.

Most of the current conversion systems between reciprocating and circular rectilinear motion (typically reciprocating motors and pumps), adopt the well known piston-connecting rod kinematic complex; this solution has all the disadvantages deriving from the presence of harmonics in the law of motion of the piston, from the lateral thrust exerted in its motion by the piston on the cylinder barrel and, finally, from the inefficient fluid dynamic use of the chamber below the piston, a chamber that is difficult to compartmentalise because occupied by the connecting rod whose head is in circular motion and whose foot is in reciprocating rectilinear motion.

For an efficient fluid-dynamic use of the chamber below the piston, as in the case of the well-known steam engines, in the past an element, called a slide, was interposed between the connecting rod and the piston, rigidly and coaxially fixed to the piston and also animated by reciprocating rectilinear motion. ; this solution, however, had the disadvantages deriving from a considerable lateral thrust imparted by the small end to the head of the slider, a significant friction on the small surface between the slider and its sliding seat, an increase in the overall dimensions of the system and in the mass of the crew in reciprocating rectilinear motion.

The following description, made with reference to the attached drawings and provided only by way of non-limiting example, will allow you to clearly understand how to carry out the invention in practice.

The present invention relates to a drive shaft consisting, in the case of single-cylinder units, of the assembly of members described below:

a) Two half-shafts (indicated by number 3 in Fig. 1, 2, 4, 5, 7, 8, 10 and 11) symmetrically placed one in front of the other on the same geometric axis of rotation and on each of which is keyed a gear, for example to the main journal; the two gears, directly or by means of further gears, mesh on the same pinion (gears and pinion all indicated by number 7 in Fig. 3, 6, 9 and 12), thus constraining the two half-shafts to rotate one in the opposite direction with respect to to the other; each of the two half-shafts is equipped with a button crank pin (cantilevered) or, on the contrary, made as a housing in which a bearing can be housed, a bearing that can be sliding, ball or roller (the latter indicated with number 9 in Figs. 3, 6, 9 and 12); in the remainder of this document, the crank pin with which each half-shaft is equipped will be defined for convenience simply as 'pin A', if in the singular, and 'pins A', if in the plural and, in any case, without apices.

b On the pin A (indicated by number 2 in Fig. 1, 2, 4, 5, 7, 8, 10 and 11) an intermediate member is pivoted (or housed), which can consist of a crank, a connecting rod or a rotor (indicated with number 1 in Fig. 3, 6, 9 and 12), free to rotate around its own rotation axis parallel to the rotation axis of the relative half shaft; each intermediate member is equipped, at the opposite end with respect to the point where it is pivoted (or housed) on the pin A, with a crank pin (indicated with number 4 in Fig. 1, 2, 4, 5, 7, 8, 10 and 11) with button (cantilever) or, on the contrary, realized as a housing in which a bearing can be housed, bearing which can be sliding, ball or roller (the latter indicated with number 9 in Fig. 3, 6, 9 and 12); in the remainder of this document, the crank pin with which each intermediate member is equipped will be defined for convenience simply as 'pin B', if in the singular, and 'pins B', if in the plural and, in any case, without apices.

The circumference described by pin B due to the rotation of the intermediate member on its axis will have a radius equal to half the radius of the circumference described by pin A due to the rotation of the relative half shaft.

c The head of a single slider is pivoted on pin B (indicated by number 5 in Fig. 2, 5, 8 and 11), whose foot is fixed coaxially to a piston (indicated by number 6 in Fig. 2, 5, 8 and 11;

The opposite rotation of the two half-shafts and of the two intermediate parts pivoted on them will determine the reciprocating rectilinear motion of the slide and the piston; the head of the slider, in fact, will follow a bicuspid hypocycloidal curve with respect to the circumference described by each pin A due to the rotation of the relative half shaft.

The aforementioned bicuspid hypocycloidal curve is described by a point of a circumference of radius ri (circumference described by pin B due to the rotation of the relative intermediate organ on its axis, center of the circumference itself), tangent to - and inscribed in - another circumference with radius r2 = 2 * ri (circumference described by the corresponding pin A due to the rotation of the relative half shaft on its axis, center of the circumference itself).

A multi-shaft system with synchronous parallel pistons can alternatively adopt a configuration with pairs of counter-rotating crankshafts.

In the case of a multi-shaft system with synchronous parallel pistons, a chain of gears will constrain the pair of half-shafts of each motor shaft to rotate integrally in the same direction; the intermediate members pivoted in the two half-shafts of the same drive shaft can, in this case, be made integral with each other or made as a single piece, thus guaranteeing their rotation in the same direction and in the opposite direction of rotation with respect to that of the half-shafts they are pivoted; however, this solution requires the addition of a rigid connection between the sliders, made in such a way as not to subject the sliders to lateral thrusts.

The operating mechanism of the invention is illustrated below in the case of single-cylinder units and the relationships existing between the movements of the various elements that compose it:

1. The piston (indicated by number 6 in Fig. 2, 5, 8 and 11), starting from its top dead center (hereinafter TDC), begins its downward stroke, pushing the slider (indicated by number 5 in Fig. 2, 5, 8 and 11) fixed to it integrally in the direction of the lower dead center (hereinafter PMI).

2 The slider, in its descent, pushes the pins B (indicated with number 4 in Fig. 1, 2, 4, 5, 7, 8, 10 and 11) in the direction of the PMI.

3 The pins B, pushed downwards by the slide, give a push to the intermediate members (indicated with number 1 in Fig. 3, 6, 9 and 12) in the direction of the PMI.

4 The intermediate members, pushed by the pins B, force the half shafts (indicated with number 3 in Fig. 1, 2, 4, 5, 7, 8, 10 and 11) to rotate, since the intermediate members are pivoted on the relative pins A (indicated with number 2 in Figs. 1, 2, 4, 5, 7, 8, 10 and 11).

5 The intermediate members, due to the thrust exerted by the slide from top to bottom on the pins B and the rotation imposed on the half-shafts by means of the pins A, in turn rotate on themselves, but in the opposite direction with respect to the direction of rotation of the respective half shafts.

6. In order to avoid non-axial thrusts being imparted to the slider due to the resistance to rotation imparted by the intermediate members, the latter rotate in the opposite direction - except in the aforementioned case of pairs of synchronous parallel pistons - and each intermediate member rotates in the opposite direction with respect to the direction of rotation of the half shaft to which it is pivoted; please note that the coordination of the rotation of the half-shafts and of the intermediate parts is guaranteed by a system of gears.

7. The combination of the rotation of the intermediate members and the rotation of the respective half-shafts in the opposite direction causes the fulcrum of the slide (indicated by number 4 in Fig. 1, 2, 4, 5, 7, 8, 10 and l i) and, with it, the slide and the piston integrally fixed to it, move linearly and alternately between the PMS and the PMI and vice versa.

Finally, the attached drawings are briefly described, the purpose of which is to suggest some possible features and the assembly of the elements making up the various solutions proposed here, by way of example and not exhaustive, for the invention.

Fig. 1 represents a front view and orthogonal to the rotation axis of the half-shafts of a single-shaft solution that uses cranks for the half-shafts and connecting rods for the intermediate members.

Fig. 2 represents a sectional view belonging to the plane of symmetry of the piston and slider assembly of a single-shaft solution that uses cranks for the half-shafts and connecting rods for the intermediate members.

Fig. 3 is an exploded representation of the component parts of a single-shaft solution that uses cranks for the half-shafts and connecting rods for the intermediate members; ball bearings, roller bearings and the relative stops (indicated respectively with numbers 8, 9 and 10) are also indicated, exclusively for greater clarity of construction.

Fig. 4 represents a front view and orthogonal to the rotation axis of the half-shafts of a single-shaft solution that uses only cranks, both for the half-shafts and for the intermediate members.

Fig. 5 represents a sectional view belonging to the plane of symmetry of the piston and slider assembly of a single-shaft solution that uses only cranks, both for the half-shafts and for the intermediate members.

Fig. 6 is an exploded representation of the component parts of a single-shaft solution that uses only cranks, both for the half-shafts and for the intermediate members; ball bearings, roller bearings and the relative stops (indicated respectively with numbers 8, 9 and 10) are also indicated, exclusively for greater clarity of construction.

Fig. 7 represents a front view and orthogonal to the rotation axis of the half-shafts of a single-shaft solution that uses only rotors, both for the half-shafts and for the intermediate members.

Fig. 8 represents a sectional view belonging to the plane of symmetry of the piston and slider assembly of a single shaft solution that uses only rotors, both for the half shafts and for the intermediate members.

Fig. 9 is an exploded representation of the component parts of a single shaft solution which uses only rotors, both for the half shafts and for the intermediate members; ball bearings, roller bearings and the relative stops (indicated respectively with numbers 8, 9 and 10) are also indicated, exclusively for greater clarity of construction.

Fig. 10 represents a front view and orthogonal to the rotation axis of the half-shafts of a single-shaft solution that uses cranks for the half-shafts and rotors for the intermediate members.

Fig. 11 represents a sectional view belonging to the plane of symmetry of the piston and slider assembly of a single-shaft solution that uses cranks for the half-shafts and rotors for the intermediate members.

Fig. 12 is an exploded representation of the component parts of a single-shaft solution that uses cranks for the half-shafts and rotors for the intermediate members; ball bearings, roller bearings and the relative stops (indicated respectively with numbers 8, 9 and 10) are also indicated, exclusively for greater clarity of construction.

Claims (2)

CLAIMS FOR THE BICUSPID HYPOCYCLOIDAL SYSTEM FOR THE CONVERSION OF THE MOTORCYCLE BETWEEN STRAIGHT LINE ALTERNATIVE AND CIRCULAR 1) A composite crankshaft consisting, with reference for example to single-cylinder units, of two half-shafts (indicated with number 3 in Fig. 1, 2, 4, 5, 7, 8, 10 and 11) symmetrically placed one in front of the other on the same geometric axis of rotation and on each of which a gear is keyed that meshes with the same pinion (gears and pinion all indicated with number 7 in Fig. 3, 6, 9 and 12) directly or by means of further gears thus binding each half shaft to rotate in the opposite direction with respect to the other, two further members (hereinafter referred to as intermediate members, each of which can consist of a crank, a connecting rod or a rotor, indicated with number 1 in Fig. 3, 6 , 9 and 12) each of which pivoted or housed in the crank pin of the relative half shaft (crank pin hereinafter referred to as pin A and indicated with number 2 in Fig. 1, 2, 4, 5, 7, 8, 10 and 11 ), and free to rotate around the p its axis of rotation parallel to the axis of rotation of the relative half shaft, finally a slider whose head is pivoted in both crank pins of the intermediate oigani (crank pins hereinafter referred to as pins B and indicated with number 4 in Fig. 1, 2, 4, 5, 7, 8, 10 and 11), since all said moving parts may be equipped with plain, ball or roller bearings (the latter indicated with number 9 in Fig. 3, 6, 9 and 12). 2) Device according to claim 1, characterized in that each intermediate member is dimensioned in such a way that, rotating on its own axis, it causes its pin B to describe a circumference with a radius equal to half the radius of the circumference that the relative half shaft, rotating on its own axis, it causes its pin A to describe, thus determining the reciprocating rectilinear motion of the head of the slide which will follow a bicuspid hypocycloidal curve with respect to the circumference described by each pin A due to the rotation of the relative half shaft. CLAIMS FOR THE BICUSPID HYPOCYCLOIDAL SYSTEM FOR THE CONVERSION BETWEEN RECIPROCATING AND CIRCULAR MOTION 1) A composite crankshaft consisting of, with reference for example to single-cylinder units, two half-shafts (as indicated with the number 3 in Fig. 1, 2, 4, 5, 7, 8, 10 and Π) symmetrically opposed one another on the same geometric axis of rotation and on each one of which is keyed a toothed gear that meshes with a same pinion (gears and pinion all indicated with the number 7 in Fig. 3, 6, 9 and 12) directly or by means of additional gears and thus tying each one half-shaft to rotate in the opposite direction with respect to one another, two additional either rotors or cranks (henceforth in this document called intermediate elements and indicated with the number 1 in Fig. 3, 6 , 9 and 12) each one pivoted or stayed in the crank pin (crank pin henceforth in this document called pin A and indicated with the number 2 in Fig. 1, 2, 4, 5, 7, 8, 10 and 11) of the relative half-shaft and free to rotate about its own axis of rotation parallel to the axis of rotation of the relative half-shaft, finally a piston rod which head is pivoted or stayed in both the crank pins of the intermediate elements (cranck pins henceforth in this document called pins B and indicated with the number 4 in Fig. 1, 2, 4, 5, 7, 8, 10 and 11), being all the above mentioned moving parts able to be equipped with plain, ball or roller bearings (the latter indicated with the number 9 in Fig. 3, 6, 9 and 12). 2) Device according to claim 1 characterized by that each intermediate element is dimensioned in such a way that, by rotating on its own axis, is to describe its pin B a circle of radius equal to half the radius of the circle that the relative half -shaft, rotating on its axis, does describe to its own pin A, thus determining the reciprocating movement of the head of piston road that will follow a hypocycloid bicuspid curve with respect to the circumference described by each one pin A due to the rotation of the relative half-shaft.