ES2818541B2 - MECHANISM TO TRANSFORM AN ALTERNATIVE RECTILINEAR MOTION INTO A CONTINUOUS CIRCULAR MOTION - Google Patents

Description

DESCRIPTION

MECHANISM TO TRANSFORM A RECTILINEAR MOVEMENT

ALTERNATIVE IN A CONTINUOUS CIRCULAR MOTION

OBJECT OF THE INVENTION

The invention, as expressed in the statement of this descriptive memory, refers to a mechanism to transform an alternative rectilinear movement into a continuous circular movement, by creating a kinematic chain that avoids the creation of lateral forces that affect the organ. that generates the reciprocating linear motion.

BACKGROUND OF THE INVENTION

An important precedent for this application is the ellipsograph or elliptical compass, attributed to Archimedes, an instrument used to draw ellipses and which is still used today, for example, in carpentry to cut table tops. The device comprises a body defined in a plane that is traversed by two mutually perpendicular slots, two pieces respectively sliding through the slots, which are connected by a rod that can rotate as the two pieces slide. The instrument includes a scribe fixed at any point on the rod, so that by fixing the body of the ellipsograph and rotating the rod, constrained by the sliding of the two pieces inside the grooves, the scribe will draw an ellipse. The parameters of the ellipse obtained will vary according to the fixing point of the tracer, being a particular case the middle position between the two sliding pieces that allows drawing a circle.

Traditionally, the mechanisms to transform an alternative linear movement into a continuous circular movement are based on the connecting rod-crank assembly. In the specific case of an internal combustion engine, the rectilinear movement of the piston is transformed into circular movement through a connecting rod and crank, the latter included in the crankshaft.

A deficiency observed in the mechanisms of the state of the art is that during the operation of the assembly formed by the piston, connecting rod, crankshaft and engine block, the connecting rod transmits lateral forces to the piston that affect the cylinder walls, causing friction losses. and wear.

EXPLANATION OF THE INVENTION

The purpose of the present invention is to eliminate the aforementioned problems, by means of a mechanism that is capable of transforming a reciprocating rectilinear movement into a continuous circular movement, for example, the reciprocating linear movement of the piston of an internal combustion engine, without generating forces. side effects that affect the organ that generates the reciprocating rectilinear movement, for example, between the piston and the walls of the corresponding cylinder.

In a basic conceptualization of the present invention there is provided a rotating disk, or inertial disk, from which first and second cores protrude from opposite surfaces of the disk. The nuclei have a cylindrical shape with their axes parallel and are located eccentric with respect to the disk, at the same distance from the center of the disk and angularly out of phase by 180° from each other. These nuclei are housed, or are received, in respective fixed-position straight channels, perpendicular to each other, and with a width slightly greater than the diameter of the nuclei, so that said nuclei can move along the channels.

The aforementioned channels are made in two fixed plates, located one on each side of the inertia disk. In this way, the disk correlates with the rod of an ellipsograph, and the center of the disk will be constrained to describe a circular path when the nuclei move into the channels. This set works in cooperation with the components that are described below that will allow to receive the alternating movement and deliver rotation in an axis.

The second core is rotatably connected, that is to say, by means of a rotary connection, to the member that produces the reciprocating linear movement, while the first core is rotatably connected to a crank aligned with the center of the inertia disk.

In turn, the crank drives a transmission shaft mounted on bearings aligned axially with the imaginary crossing point between the channels (the crossing is imaginary or projected since the channels are in parallel planes), so that the crank accompanies the center of the disc. of inertia while describing a circumferential movement around the imaginary crossing point between the channels.

In operation, the actuation of the mechanism by means of an alternative movement allows the movement of the first and second nuclei through the channels, while the inertia disk rotates on its axis and describes a circumferential movement around the imaginary crossing point between the channels, so that said circumferential movement is transferred by the crank to the transmission shaft.

To the above, internal and external auxiliary inertia discs are added that serve as support for the connection of the nuclei to the organ that produces the reciprocating linear movement and to the crank. In addition, a 45 degree rotation of the set of channels is introduced, so that that the reciprocating movement that activates the mechanism forms an angle of 45 degrees with respect to the axis of symmetry of each channel.

In a broader conceptualization, a mechanism is described to transform a reciprocating rectilinear movement into a continuous circular movement, so as to avoid the creation of lateral forces that affect the organ that generates the reciprocating rectilinear movement. The mechanism comprises two symmetrical mechanism portions with respect to a plane of symmetry that passes through a rod that moves with the reciprocating rectilinear movement including, in which each portion a central connecting member with two opposite surfaces arranged vertically from which a first and second core respectively. Said nuclei have a cylindrical shape with their axial directions parallel; fixed plates arranged vertically on each side of the central connector member have respectively formed a first channel and a second channel, straight, with a width greater than the diameter of the cores and perpendicular to each other, where the first and second cores are received with possibility sliding along said first and second channels respectively; an inner connector member with two opposite surfaces arranged vertically is joined by one of them to one end of the second core and by the other surface projects a cylindrical pin whose axial direction is parallel and equidistant with respect to the first and second cores, and where the crankpin receives the stem; an outer connecting member with two opposite surfaces, arranged vertically, is attached by one of them to the distal end of the first core and by the other projects a bearing support, in which the axial direction of said bearing support is in a same plane , is parallel and equidistant with respect to the first and second nuclei; and a crank mounted between the bearing bracket and an output shaft to transfer continuous rotation.

In a modality of the above mechanism, each bearing support is made up of two parts, one of which is a counterweight cap that is removably fixed for mounting the crank and that has semicircular parts, the set of said parts equaling in weight to a set of pieces that move with reciprocating rectilinear movement.

Preferably the rod is integral with the piston.

In another embodiment of the mechanism described, a flywheel coupled to the output shaft is also included.

In another embodiment, constituting an alternative mode of inertia accumulation, each connector member is disk-shaped with the centers of disks aligned with each other and aligned with the axial direction of the crank. The mechanism thus obtained, furthermore, comprises that the first and second cores project from equidistant positions from the disc center of the central connecting member and angularly displaced by 180° relative to each other.

In a specific aspect of the mechanism of the invention, the axial distance between the crank and the output shaft is half the axial distance between the cores and equal to the axial distance between the crank and the crank.

In an embodiment including a counterweight cap, the distance between the center of mass of the semicircular parts and the axial direction of the crank is half the axial distance between the cores and equal to the axial distance between the crankpin and the crank .

In another specific aspect of the mechanism of the invention, the output shaft is mounted on bearings aligned axially with a point of imaginary crossing between the first and the second channel.

In another embodiment of the present mechanism, the crankpin, connector members, hubs, and bearing supports form a single piece.

DESCRIPTION OF THE DRAWINGS

To complement the description that is being made and in order to help a better understanding of the characteristics of the invention, this specification is attached, as an integral part thereof, a set of plans in which, for illustrative and non-limiting, the following has been represented:

The FIG. 1 is a front view of the kinematic chain that constitutes the mechanism associated with a piston with reciprocating linear movement, according to one embodiment of the invention.

The FIG. 2 is a right side view of the mechanism of the previous figure including a partial section in the upper right corner of the fixed plate.

FIGS. 3A, B, C and D are sectional views corresponding to the section lines drawn in FIG. one.

The FIG. 4 presents a side view of the mechanism of FIG. 1 with the piston at top dead center.

The FIG. 5 is a partial sectional view according to line H-H of the previous figure, where the following has been excluded from the section: crank, transmission shaft and bearing thereof.

The FIG. 6 is a partial sectional view along the line II of FIG. 4, in where it has been excluded from the cut: crank, transmission shaft and bearing thereof.

The FIG. 7 is a perspective view according to the embodiment of the invention represented in the previous figures.

FIGS. 8A, B, C and D are perspective views associated with the previous figure, in which two plates with channels for guiding the cores have been omitted, thus allowing to appreciate the relative positions of the latter for different angles of rotation of the crank. (180°, 270°, 315°, 360° respectively).

FIGS. 9A, B, C and D are schematic representations showing the relative positions of the axial directions of the crankpin (point A), the crank (point C) and the center of mass of the counterweight cap (point B) for different angles. crank rotation (0° or PMS, 90°, 180° or PMI, and 270° respectively).

The FIG. 10 is a front view of the kinematic chain that forms the mechanism associated with a piston with reciprocating linear movement, in another embodiment of the invention.

The FIG. 11 is a right side view of the mechanism of the previous figure including a partial section in the upper right corner of plate 10.

FIGS. 12A, B, C and D are sectional views corresponding to section lines drawn in FIG. 10.

The FIG. 13 presents a side view of the mechanism of FIG. 10 with the piston at top dead center.

The FIG. 14 is a partial sectional view according to line H-H of the previous figure, where the following has been excluded from the section: crank, transmission shaft and bearing thereof.

The FIG. 15 is a partial sectional view along the line I-I of FIG. 13, where the following has been excluded from the cut: crank, transmission shaft and its bearing.

The FIG. 16 is a perspective view according to the embodiment of the invention shown from FIG. 10.

The FIG. 17A corresponds to an embodiment of the bearing support formed by two portions for mounting the crank, the first portion is integral to an external disk and the second comprises a cap with a counterweight.

The FIG. 17B is a top view of the cap of the previous figure.

FIGS. 18A, B and C show by dashed lines a proposed lubrication system for an embodiment with disk-shaped connecting members.

The FIG. 19 corresponds to an exploded view of an example of embodiment for the assembly formed by a piston-rod assembly and other parts that move with reciprocating movement; Said parts including two bearing shells, a cap, two washers and two union bolts.

The FIG. 20A is a sectional view of the piston-rod along section line TT drawn in FIG. 19, passing through the lubrication segment.

The FIG. 20B is a side view of the piston-rod depicted in FIG. 19, which includes two compression ring grooves and one oiler ring groove.

The FIG. 20C is a view of detail U of the piston-rod shown in FIG. 19.

The FIG. 20D is a top view of the bonnet depicted in FIG.

19.

The FIG. 21 is a perspective view according to the embodiment of the invention shown from FIG. 10, in this case including counterweights on the cranks.

PREFERRED EMBODIMENT OF THE INVENTION

The accompanying figures show different modalities and examples of embodiments for various components of the mechanism according to the present invention, having used, for each of its parts, the numerical references indicated in the following list:

3, 3' first core

4, 4' second core

8a, 8a' outer connector member

8b, 8b' central connecting member

8c, 8c' inner connector member

9a, 9a' outer connector member (disc-shaped)

9b, 9b' central connector member (disc-shaped)

9c, 9c' inner connector member (disc-shaped)

10, 10' fixed plate

11, 11' fixed plate

12 crankpin

13 stem cap

14 stem

15 piston

16 16’ mechanism halves

18 crank

19 output shaft

20, 20' bearing bracket

20th bearing bracket integral portion

20b counterweight cap

20c semicircular parts (of the counterweight cap)

21 rest (output shaft)

A first embodiment corresponds to FIGS. 1 to 7, while a second embodiment is presented in FIGS. 10 to 16 (through views similar to FIGS. 1 to 7). In each mode, the mechanism of the present invention is associated with a rod (14) and a piston (15) belonging, for example, to an internal combustion engine, movable with reciprocating rectilinear movement. In addition, in the aforementioned figures, the mechanism has been represented when the piston (15) is located at the top dead center (TDC). Additionally, the progression of rotation of the mechanism is illustrated in FIGS. 8A to 8D for four angular positions, specifically at bottom dead center (BDC), at 270°, at 315° and at top dead center (TDC),

For illustrative purposes, the mechanism is conceived as consisting of two halves (16, 16') that present symmetry with respect to the median plane of the rod, represented by the section line DD in FIGS. 1 and 10. In each half there are fixed parts 5 such as the plates (10-11 and 10'-11') and mobile parts such as the connecting members (simple: 8a, 8b, 8c and 8a', 8b', 8c'; or disk-shaped: 9a, 9b, 9c and 9a', 9b', 9c') and some nuclei (3, 4 and 3', 4') attached to the latter. Furthermore, the two halves of the mechanism are thus joined together through the pin (12). Note that the symmetry of the mechanism is not an obligatory condition, but by virtue of it and for illustrative purposes the description of the mechanism will be done as far as possible with reference to components of one of the two halves.

In the sectional views of FIGS. 3D and 12D show the stem (14) rotatably connected to the crankpin (12) which can move with reciprocating movement. While in FIGS. 3A and 12A, it is shown that a bearing bracket (20) receiving a crank (18) is formed on the outer surfaces of connector members located at outer positions (for example, 9a), to transfer continuous rotation to the output shaft. (19). Thus, the bearing support (20) is rotatable since it rotates or moves with a circumferential trajectory with respect to the output shaft (19).

Before continuing to describe the kinematic chain, a series of aspects must be qualified. For this, reference is made to the configuration suggested in FIGS. 19 and 20A to 20D. The piston (15) acquires a peculiar shape because it lacks a skirt and is provided with a long rod (14), necessary to be able to assemble it with the pin (12). The rod will be made of the same material as the piston, for example, an aluminum alloy, and the length shown is necessary when the embodiment used corresponds to that shown in FIGS. 10 to 16, because the piston must not interfere in the space occupied by the disc-shaped connecting members. In conclusion, in a preferred embodiment, the piston and rod constitute a single piece. Furthermore, FIGS. 20A to 20D present constructive details as suggestions for the rod-piston assembly, respectively: a cross section is made through a piston lubrication segment, it is shown how the rod has a flattened shape in the transverse direction of the mechanism, a way of fixing the half-bearings in position is suggested, and the union of the stem to the pin (12) by means of a cap (13) is proposed.

Going back to the description of the components of one half (16) of the mechanism, the way in which connector members and cores are joined can be appreciated either by the sequence of sectional views of FIGS. 3A to 3D or 12A to 12D as by the sectional views of FIGS. 5, 6, 14 and 15. In particular, each half of the mechanism comprises three connecting members, which can have a shape directed only to the joining function, like the connecting members (8a, 8b, 8c), or incorporate the function kinetic energy storage as the connector members (9a, 9b, 9c) shaped like an inertia disc. Regardless of the way the connector members have, they are located in an alternate position with respect to the fixed position plates (10, 11), one exterior or distal to the stem (connector member 8a or 9a), another in the center (connector member 8b or 9b ) and, the third, interior or proximal to the stem (connecting member 8c or 9c). Between the central connecting member (8b, 9b) and the outer and inner connecting members (8a and 8c or 9a and 9c) the cylindrical cores (3, 4) are projected perpendicularly, eccentric (180° out of phase) and at the same distance from the center of the connecting members.

Given the arrangement of the elements to be connected, when the connector members do not have a disc shape, they will be different in shape from each other. That is, the inner connecting member (8c) that is attached to the crank pin, the central connecting member (8b) that is attached to the two cores (3, 4) and the outer connecting member (8a) that is attached to the support of swivel bearing have different shapes, as seen in FIGS. 8A-8D.

To complete the configuration described, the nuclei (3, 4) pass through the plates (10, 11) through channels that they have made on their diagonals, as shown in FIGS. 2, 3B and 3C or in FIGS. 11, 12B and 12C. The channels have their fixed position, are perpendicular to each other by superimposing both plates, and have a width slightly greater than the external diameter of the nuclei (3, 4) so that they can move along the channels.

Referring to FIGS. 2 and 11, it can be seen that the lines of symmetry of the channels, projected from the corners E and F, intersect at point G, which is aligned with the output axis (19), while the central axis of the connecting members, aligned with the crank (18), can rotate around point G.

Although it is possible to define the position of the channels so that one is parallel to the direction of movement of the piston (15), for the preferred embodiment it has been decided to rotate them by 45 degrees. In addition, the channels must have a length greater than or equal to the stroke of the piston (15).

Angularly shifting the slots is only possible if a number of conditions are met:

• The crank should be one quarter of the length of the piston stroke.

• From the junction point of the crank with the connecting members to the crank pin, it must have a length of one quarter of the piston stroke.

• The length between centers (ie, the axial directions) of the cores is equal to half the stroke of the piston.

• The distance from the axis of the nucleus (3) to the pin (12) of the piston is equal to the hypotenuse of a triangle whose legs have the length of a quarter of the piston stroke.

In any case, then, preferably, the axial distance between the cores (3 and 4) is equal to half the distance of the piston rod stroke, and, for its part, the axial distance of the pin to any one of the nuclei (3, 4), is equal to the hypotenuse whose legs have the distance of a quarter of the piston-rod stroke.

Referring to FIGS. 6 and 15, the axis that passes through the crank (18) is located exactly between the axes of the cores (3 and 4), that is, said crank is located at the same axial distance from both cores. Furthermore, in FIG. 15, the axial directions of the crank (18), the disk-shaped connecting members (9a, 9b, 9c) and the bearing bracket (20) are coincident.

It is also established that the distance between the crank axis (18) and the output axis (19) is half the distance between the cores (3, 4), and equal to the distance between the crankpin axis ( 12) and the crank shaft (18).

As previously indicated, in operation the circumferential movement of the connecting members (8a-8c; 9a-9c) is recorded around point G, while they rotate around their axis, all of this by virtue of the restriction to displacement or guiding of the nuclei (3, 4) into the channels in the plates (10 and 11).

Emphasis is placed on the fact that the crank pin, connecting members, hubs and bearing brackets form a single piece. As mentioned before, the disc-shaped alternative for the connecting members (FIGS. 10 to 16) is associated with the storage of kinetic energy, but also with the reinforcement of the union between the cores (3, 4). For On the other hand, a conventional flywheel may be additionally connected, for example, adjacent to the rest (21) of the output shaft (19), which will be especially appropriate when non-disk-shaped connector members are used.

In another aspect of the invention, with reference to FIGS. 17A and 17B, in order to compensate for the force of inertia produced by the reciprocating parts in their displacement, a counterweight can be arranged on each outer connecting member (9a, 9a'). As can be seen, the mechanism comprises a counterweight cap (20b) which is the joining part of the bearing support (20), being provided with semicircular parts (20c), of which its center of rotation can be found. gravity in a simple way and whose objective is to increase the mass to the extent necessary for the counterweight. The set of parts of the counterweight cap (20b) has a center of gravity that coincides with the point that acts as a counterweight to the set of moving parts of the piston with a rod. The weight of the semicircular parts (20c) belonging to two caps is equivalent to the weight of the parts that move with reciprocating rectilinear movement together with the piston and rod. Referring to FIG. 19, the set of parts from which the weight should be calculated, to determine the dimensions of the semicircular parts (20c) of the counterweight cap (20b) includes: piston, rod, rod cap, two semi-bearings, two washers , a lubrication ring, two compression rings, two union bolts and the crank pin (12).

Referring to FIGS. 9A to 9D below, the theory that supports the location and application of the counterweight cap is exposed. The figures represent a circle in a dashed line and three points located on a straight line, designating each of the points with a letter. Each point represents the center of mass of one or more components, specifically: point A corresponds to the crankpin (12), point B corresponds to the counterweight (as already indicated, balanced so that its weight is equal to the reciprocating parts next to the piston and rod), point C It corresponds to the rotating connection of the disk-shaped connection members with the crank and therefore the center of the disks, which in turn moves circularly on the trajectory represented by the dashed circumference.

In FIG. 9A the piston is at TDC, FIG. 9B is in the middle of the piston stroke, FIG. 9C represents when the piston is located at BDC and FIG. 9D is three-quarters of the way down the piston, on its way to a full revolution. It should be noted that points A and B always move linearly and alternately, unlike point C which does so circularly.

Furthermore, the schematics of FIG. 9A to 9D include arrows that represent forces of inertia, which we will detail below.

When point A is at TDC, the inertia force of point A has a value of zero with respect to the initial direction, as long as the weight of point A is equal to the weight of point B, because previously, along its mid-race run to PMS has transmitted all the inertia force it possessed to point B, point B being at that very instant the one with the maximum value of inertia.

When point A is in the middle of the race, the inertia force of point A has a maximum value with respect to the initial direction because previously, throughout its travel from TDC to the middle of the race, it has acquired all the inertia force that point B possessed, being the inertia of point B at that same instant of zero value, as long as the weight of point B is equal to the weight of point A.

When point A is at BDC, the force of inertia of point A has a value of zero with respect to the initial direction, as long as the weight of point A is equal to the weight of point B, because previously, along During its mid-travel journey up to the PMI, it has transmitted all the inertia force it possessed to point B, being point B at that same instant the one with the maximum value of inertia. And so on throughout a full turn of the crank.

When point A is at PMS, it has been possible to transmit all the inertia force from point A to point B, due to the angular movement that is made from one point to another during its movement.

It must be taken into account that the connections, the inertia disks and the cores must comply with the theory that has been described. The exposed theory is the reason why with a correct balancing of the counterweight, with respect to the piston with rod, there should not be forces of inertia contrary to the direction of rotation of the crank. And therefore it constitutes an important advantage of the present invention.

This theory affects all the parts that make up the kinematic chain of this invention, except for the crank and the block that contains said set of links. Once the movement of the parts of which it is composed has been defined, it is opportune to make a reminder regarding two very simple definitions on physics; are the following:

- Center of gravity of a body: It is the point where the calculation of the gravitational moment can be considered that the force of total gravity acts, that is, it is equivalent to the sum of all the points of the body that exert a force of gravity, affecting the set of all of them in a single point located at an average distance proportional to the force of gravity of all the points.

- Center of rotation of a body: Point around which a body rotates at a given instant. It is defined as the intersection of the perpendiculars to the trajectories that the points of the moving body cover.

In the theory, the points defined as A, B and C correspond to certain centers of gravity: Point A, is the center of gravity according to its direction of travel, of all the elements that make up point A. Point B, is the center of gravity according to its direction of displacement, of all the elements that make up point B. Point C, is the center of gravity of the elements that make up point C, on which points A and B affect.

It is necessary to define where the center of rotation of the set of points A, B and C is located. For this, point A could be useful, when it is located at TDC, but point B could also be useful, when it is it is located in its position with respect to the half of the route of point A, both in one case and in the other, in the situation that has just been considered of point A and B, tracing a circle whose center is equivalent to the center of the circle that describes the path of point C, but whose radius is equal to half the path that both point A and point B make. In said circumference periphery, the center of rotation of the set of points A, B and C is obtained, the which has the particularity that it maintains a constant change on the point that it exercises as the center of rotation, during the movement of the entire set.

Since the center of rotation of any body is of inertia=0,

where I=moment of inertia, m=mass, r=radius, the center of rotation of a body has r=0, therefore:

This last definition explains the reason why point A, when it is located at TDC, has zero kinetic energy and the same occurs at point B when it is located in the middle of the race. This assessment of the mechanism is of considerable importance, especially referring to the fact that when we try to extract favorable performance from a machine, inertia forces contrary to the direction of rotation are normally produced. Since at point A all the inertia of the elements moving in that direction will transmit their inertia to point B as a result, the force exerted by the gases at the moment of the explosion will be exerted on a point free of forces of inertia contrary to the direction of its displacement, in combination with the inertia force exerted by the mechanical components that act towards an established direction of rotation, above all, the loss of performance due to friction forces will be calculated.

In another aspect of the invention, presented in FIG. 18A to 18C a suggestion for a lubrication circuit, including three views of the assembly formed by connector members (in the form of inertia discs), cores and the crankpin. In the part that includes the connecting members, the oil conduit necessary to lubricate the pin and half-bearings of the part that is assembled from the stem can be seen. You can also see the fixed parts of the supports bearing bushings (20a) located each on both sides of the outer discs.

A person versed in the technical field of this invention will note that there are multiple embodiment options for the mechanism thereof, in particular, the following options are noted for the set of elements intended to provide inertial forces:

a) A mechanism consisting of a kinematic chain equipped with a flywheel, connecting members in the form of inertia discs and a counterweight cap (20b) on the bearing support (20).

b) A mechanism consisting of a kinematic chain provided with connecting members in the form of inertia disks and a counterweight cap (20b) on the bearing support (20).

c) A mechanism consisting of a counterweight cap (20b) on the bearing support (20) equal in weight to the piston, stem and other parts that move with reciprocating motion.

d) A mechanism consisting of a flywheel and a counterweight cap (20b) on the bearing support (20).

EXAMPLE 1

Bearing in mind that the channels have the same length as the piston stroke, to determine the diameter of the cores, a circumference perimeter equivalent to twice the piston stroke must first be calculated, thus obtaining that a part of the core is rolling on the carcass, while the other part must necessarily produce friction when in contact with its corresponding channel, so it must remain bathed in oil.

In the first place, once the length of the piston stroke has been determined (for example, 80 mm), the circumference formula is applied, in which, having the circumference of the circumference, the radius is found.

Piston stroke= 80mm

Perimeter of the circumference= 80 mm x 2= 160 mm

Radius= 160mm/ (2-n)= 25.46mm

Core diameter= 50.92 mm

EXAMPLE 2

If a larger diameter for the cores is necessary for technical reasons, this would also be accommodated in the design of the mechanism. Determining a perimeter of the circumference equal to twice the stroke of the piston, has the purpose of obtaining less friction losses.

Therefore, if an axis whose diameter is increased proportionally is used, without taking into account its relationship with the piston stroke, what will happen is that friction will increase, which must be solved so that said axis is bathed in oil

In order to broaden the understanding of the object of the invention, it is worth emphasizing some aspects and particularities of the mechanism.

The centrifugal force of the inertial discs of this kinematic chain, due to the direction in which the discs rotate, around the center of rotation of the crank as well as on the same center of rotation of the discs, the combination of both movements gives as a result, that the centrifugal force obtained by the discs, is produced around the center of rotation of the crank, in the direction towards the center of rotation of the crank, due to the situation of the center of rotation of the inertia discs, which is displaced and proportionally far from the center of the same disc, but still at a greater distance than the center of rotation of the crank. Regarding all these aspects, it must be emphasized that the direction of rotation of the inertia discs of this kinematic chain is carried out in the opposite direction to the direction of rotation of the crank, and due to the joint action of the two movements, it gives as As a result, as previously indicated, the centrifugal force of the discs is carried out in the direction of the center of rotation of the crank.

The reason that gives rise to the description made, in addition to the particular movement of the inertial discs, is due to the fact that in the direction in which the centrifugal force is produced, it corresponds to the direction in which the discs have a greater volume in relation to their center. of rotation.

- Counterweights of the inertia discs.

The circumstance explained in the previous paragraph must be compensated with the incorporation of some counterweights that are part of the cranks, depending on the number of cylinders and their arrangement with respect to their configuration such as engine-block, V-shaped cylinders, online etc

The aforementioned counterweights must have characteristics with values of mass and center of gravity as a whole, equal to the values that cause the centrifugal force of the set of inertia discs, but that in the case of the counterweights, the centrifugal force is oriented in the opposite direction to that of the discs, compensating their action and providing vibration-free operation.

An exception related to engines that could have a kinematic chain like the one in this patent, without the need to incorporate counterweights intended to compensate for centrifugal force. of the inertia discs, it would be a four-cylinder in-line engine with a flat crankshaft, which is widely used, whose arrangement of the pistons, when two of them, referring to the two that are located at the ends in the longitudinal direction of the engine-block, or to the other two pistons located in the middle part of the engine-block, just as one pair of them is in the top dead center, the other pair of pistons is in the bottom dead center. This arrangement transferred to the case of this kinematic chain, in which each piston-rod has its own inertia discs, results in the total set of inertia discs corresponding to all the piston-rods of a four-cylinder in-line engine block, the centrifugal force produced by these will be compensated with this arrangement of the pistons with rod, because half of the total discs are facing the other half, establishing an exact balance in the operation of all the elements that are connected. composes, thanks to the compensation of the masses of the discs from any angle, providing a homogeneous operation of all the mechanical elements.

- Part of the inertia disc that generates centrifugal force.

To determine the part of the inertial disk that generates centrifugal force, first of all, two clearly differentiated areas must be identified on the circumference area of the disk, because each one of them forms a part of the disk with a different function from the other. , separating the area that will form part of the disc, providing inertia, but that at that moment during the operation of the entire mechanical assembly does not generate centrifugal force, giving rise to the rest of the area of the disc, if it belongs to that part that at that time same instant generates centrifugal force.

To carry out the following description, it is necessary to take the diameter of the inertia disk with which a circle must be drawn on a plane, on the center of the circumference, drawing an axis of symmetry from the top to the bottom of the plane dividing the circumference into two symmetrical parts. Having marked a point in the center of the circumference, with an upwards direction of the plane, it is necessary to take the measurement corresponding to half of the stroke of the piston-rod, marking the aforementioned measurement with another point on the axis of symmetry made.

In the middle of the measurement described above, another point must be marked, which corresponds to the center of rotation of the inertia disk. An axis of symmetry perpendicular to the first must be drawn on this last point.

With the description made, two axes of symmetry are obtained, one has been drawn from the top to the bottom of the plane and the other horizontally to the plane, the latter passing through the midpoint (center of rotation) of the other two.

On the marked points, first the point that is above the plane must be taken, at this point another circle with the same diameter as the inertia disk is drawn, but only the part of the circle that coincides with the first is marked. made, without the need to draw the entire circle, because the section that is necessary to take is the one that corresponds to the inner part of the circumference of the disk.

In this way, two differentiated areas are determined, which have the same center of rotation, but just as one of them is symmetrical to the horizontal axis of symmetry that passes through the center of rotation, the other is displaced to one side of said center. , being the area of the latter the one that determines the part of the inertia disc that generates centrifugal force.

It is necessary when the diameter of the inertia discs has been established, to find the value of the center of gravity of this displaced part of the discs, to incorporate some counterweights with the same value of mass. and center of gravity on the cranks of this kinematic chain, whose centrifugal force of the counterweights can compensate the vector generated by the centrifugal force of the discs.

The area that is located on one side of the center of rotation of the inertia disk, multiplied by the length of the disk, are the necessary data to obtain the volume as a result to determine the mass, and whose center of gravity is the cause of the centrifugal force of the inertia disk.

The part of mass obtained corresponding to a single disc, with a total of six discs in the kinematic chain presented, must be divided by two, said quantity multiplying the result by the mass indicated above.

The value of the mass and the center of gravity corresponding to the part of the disc located to one side of the center of rotation, of the three discs that have been indicated, are necessary to determine the same values for a single counterweight that forms part of a of the cranks, being the same for the other crank of which the mechanism is composed, corresponding in this case to the three remaining discs.

- Kinetic energy of the inertia discs.

Regarding the accumulation of kinetic energy of the inertial discs, the two different parts of the disc play a fundamental role, each of which fulfills a different function.

One of the parts is the one that is defined in relation to the center of rotation, on which an axis of horizontal symmetry must be drawn with respect to the plane, obtaining a part of the disc characterized by being symmetrical to said axis, and which also has the particularity of which accumulates a corresponding part of the inertia of the disk.

The other part of the inertia disk is that which, having traced an axis of horizontal symmetry with respect to the plane, which passes through the center of rotation of the disk, it is away to one side of the center of rotation and therefore it is not symmetric with respect to the horizontal axis of symmetry that passes through said center. This part of the disc, during the operation of the kinematic chain, accumulates kinetic energy, which affects in a particular way on the plane that the channels have, providing a wide variety of options regarding the operation of the mechanical assembly, related to the diameter of the discs. of inertia.

This characteristic depends on numerous factors, such as the space available for each element, as well as, on the other hand, establishing the capacity of the efficiency obtained by mechanics. All this supposes a series of conditions to be determined, whose approach is possible thanks to the idea of this invention.

- Center of rotation of the translation of the inertia discs.

The inertia discs, at the same time that they make a turn about the center of rotation, also make a translation movement around the same center of rotation as that of the crank.

The translation movement of the inertia disks is described as point C in the body of this report, for the purpose of performing the pertinent calculations that affect a body in motion, taking into account the center of rotation of the inertia disk. inertia, and in the case of this patent the center of rotation of the translation of the inertia discs.

It is necessary to know the translational movement carried out by the inertia discs, which progressively determines the position of the discs during the completion of a turn, turning around the center of translation for one turn around the center of rotation, having to differentiate each one of the movements for the correct realization of the calculations.

When specifying the two differentiated parts of the inertia disks, the part symmetrical to the axis of symmetry horizontal to the plane that passes through the center of rotation and the part displaced to one side of the center of rotation, it is necessary to take the relative reference to the center of rotation of the disc to obtain the corresponding results, however the translation movement they perform will be necessary to specify the angle of the disc, especially in relation to the point of support of the nuclei with the channels and the direction in which the forces act, taking into account the distance where the force is produced to the point of support.

- Fixing of the channel plates.

The plates that contain the channels through which the cores of this kinematic chain move, must be solidly attached to the engine block.

The example that is going to be exposed does not limit in this aspect other possibilities that could form part of the mechanism, such as mechanical elements that fulfill the function of the channels.

The mechanical concept described consists of a design made of steel plates, which must fit exactly inside the crankcase corresponding to the engine block. It is necessary to point out that each of the plates consists of two parts, an upper part and a lower part, the upper part will remain fixed to the engine block by means of a weld, the lower part will be fixed to the upper part of the plate and block -motor by means of the corresponding screws, facilitating the assembly/disassembly of the inertia discs, as well as the set of all the pieces of which the kinematic chain consists.

Referring to the screws that must fix the lower part of the plate, both these and the environment where they must remain firmly attached, must not interfere with the path made by the inertia discs, allowing the discs to have the necessary space to fulfill its function.

By joining the upper plate with the lower one, the space can be appreciated destined for the channel, where the nuclei carry out their displacement. At the ends of the channel, the half-circumference shape is detailed, necessary for the core to have a place in that part of the channel, leaving a certain distance so that the core does not touch the walls of the channel in the half-circumference area, while Contrary to that in the flat areas of the channel, where the nuclei are in contact with the channels, although with tolerance to be able to slide through them.

You can also appreciate the inclination of the channel, which, as is already known, a pair of them will be made at 45° with respect to the axis of symmetry that passes through the piston-rod, and the other pair of channels will be at 45° of said axis of symmetry, but at 90° to the first pair of channels described.

The parts that are in contact of the upper and lower plate of the channels, those that are close to the channel, being of a certain length and with a linear surface, are provided with a longitudinal guide at their distance, with the function that when Being attached to the upper and lower part, these guides solve the forces transversal to the plane of the channel, which could occur during the operation of the mechanism.

- Characteristics.

Of the possibilities provided by the kinematic chain described in this patent, it is worth highlighting the example of the mechanism that consists of a flywheel, the corresponding six inertia discs necessary for a piston-rod, and the parts that act as a counterweight. of the piston-rod, as the option for the best possible result provided by this invention.

As a relevant aspect of this mechanical assembly, perhaps the most important, it should be noted the use that results from the force produced by the ignition of gases at the time of its expansion, just when the piston-rod is at the top dead center, that is, when the pressure of the ignited gas is higher. This force falls in a downward direction on a 45° inclined plane, corresponding to the channels. This supposes at this moment a use of 70% of the force generated, at the moment in which the magnitude of the ignition of the air-fuel mixture is higher.

When the explosion occurs in the combustion chamber of the cylinder head, the piston-rod transmits the force generated linearly towards the downward direction of its travel, which it carries out inside the cylinder.

The piston-rod remains attached by a revolute joint to the inertia discs, and then at the aforementioned moment of combustion, the two cores 4 and 4' transmit all the force applied to the 45° inclined plane that forms their corresponding channels. . Said force must be multiplied by the cosine of the angle composed by the direction of the force with respect to the inclined plane (angle=90°-45°=45°), on which we obtain a resulting force of 70% of the total. Obtaining this force at this very moment, thanks to the values of the angles belonging to their corresponding planes, allows the resultant to be transmitted in the same magnitude towards the other two nuclei 3 and 3', following the latter in a direction towards the crank.

Due to the data of the previous description, the importance of the performance of this kinematic chain is justified, highlighting the reason why the axis of symmetry of the piston-rod must be displaced at 45° from the axes of symmetry of the channels.

The benefit of this circumstance is achieved in the first instance, thanks to the inertia of the discs in the direction of rotation, whose force affects in relation to the 45° inclined plane of the channels in the downward direction, favoring the expansion force to contribute performance in a four-stroke cycle, within parameters that are not they get in other mechanisms.

The purpose of a purpose like this is the reduction of consumption, and the feasibility of facing the possible use of ecological fuels.

- Advantages

As can be seen in the description of this kinematic chain, the connecting rod is dispensed with to carry out the transformation of the reciprocating rectilinear movement into continuous circular movement, with which the piston is free of lateral forces, performing a more uniform sliding on the walls along its path. of the cylinder, thus avoiding friction losses and reducing wear.

When the piston begins to descend from top dead center to bottom dead center, a rotational force is produced at the same time that the cores move inside the channels. At the moment in which the expansion occurs, the forces that increase due to it, go after and in the same direction as those that had initially produced the forces of inertia, for this purpose to be possible, a series of additional calculations that remain outside the patent, the contribution of these determines the mass of each of the links of this kinematic chain, producing a force of greater intensity than in a piston, connecting rod, crankshaft and block kinematic chain.

The incidence of the forces that act on the axes of the nuclei, with respect to their corresponding channels, form an inclined plane at forty-five degrees of the related force in each case.

During the expansion time there is a better use of the gas pressure because the forces acting on the shafts and crankpins do so with greater intensity than in a piston, connecting rod, crankshaft and block powertrain.

A more homogeneous friction is obtained in the upper part of the piston, which is in contact with the ignition of the gases, so that the piston better supports high operating temperatures.

Due to the existence of the channels, they will support the bending stresses produced by the connecting members and the piston on the cores, therefore the cranks will be free of bending stresses and will only have to withstand torsion stresses.

Claims (12)

1.- A mechanism to transform a reciprocating rectilinear movement into a continuous circular movement, so as to avoid the creation of lateral forces that affect the organ that generates the reciprocating rectilinear movement, characterized in that it comprises two symmetrical portions of the mechanism with respect to a plane of symmetry that passes through a rod (14) that moves with the reciprocating rectilinear movement, in which each portion includes: - a central connector member (9b) with two opposite surfaces arranged vertically from which project a first and a second core (3, 4) respectively, said cores having a cylindrical shape with their axial directions parallel; - some fixed plates (10, 11) arranged vertically on each side of the central connector member (9b) which respectively have formed a first channel and a second channel, straight, with a width greater than the diameter of the cores and perpendicular to each other, in where the first and the second core (3, 4) are received with the possibility of sliding along said first and second channels respectively; - An internal connector member (9c) with two opposite surfaces arranged vertically, one of them joining one end of the second core (4) and a cylindrical pin (12) projecting from the other surface whose axial direction is parallel and equidistant with with respect to the first and the second core (3, 4), and where the pin (12) receives the rod (14); - An outer connecting member (9a) with two opposite surfaces, arranged vertically, one of them joining the distal end of the first core (3) and a bearing support (20) projecting from the other, in which the axial direction of said bearing support is in the same plane, is parallel and equidistant with respect to the first and to the second kernel (3, 4); Y - a crank (18) mounted between the bearing support (20) and an output shaft (19) to transfer continuous rotation. 2. - The mechanism according to claim 1, characterized in that each bearing support (20) is made up of two parts, one of which is a counterweight cap (20b) that is removably fixed for mounting the crank (18) and that It has semicircular parts (20c), the weight of the set of said parts being equal to a set of pieces that move with the reciprocating rectilinear movement. 3. - The mechanism according to claim 1, characterized in that it further comprises a flywheel coupled to the output shaft (19). 4. - The mechanism according to claim 1, characterized in that the rod (14) is integral with a piston (15). 5. - The mechanism according to claim 1, characterized in that each connector member (9a, 9b, 9c) is shaped like a disc with the disc centers aligned with each other and aligned with the axial direction of the crank (18). 6. - The mechanism according to claim 1, characterized in that the first and second cores (3, 4) project from equidistant positions from the center of the disc of the central connector member (9b) and are angularly displaced 180° from each other. 7. The mechanism according to any of the preceding claims, characterized in that the axial distance between the crank (18) and the axis of outlet (19) is half the axial distance between the cores (3, 4) and equal to the axial distance between the crankpin (12) and the crank (18). 8. The mechanism according to claim 2, characterized in that the distance between the center of mass of the semicircular parts (20c) and the axial direction of the crank (18) is half the axial distance between the cores (3, 4 ) and equal to the axial distance between the pin (12) and the crank (18). 9. The mechanism according to any of the preceding claims, characterized in that the output shaft (19) is mounted on bearings axially aligned with an imaginary crossing point between the first and the second channel. 10. The mechanism according to any of the preceding claims, characterized in that the pin, the connecting members, the cores and the bearing supports form a single piece. eleven.

- The mechanism according to any of the preceding claims, characterized in that the axial distance between the cores (3 and 4) is equal to half the distance of the piston-rod stroke. 12. - The mechanism according to any of the preceding claims, characterized in that the axial distance from the crank pin to any one of the nuclei (3, 4), is equal to the hypotenuse whose legs have the distance of a quarter of the piston stroke -stem.