WO2007080623A1

WO2007080623A1 - All terrain vehicle with driving means such as wheels or tracks mounted on articulated legs

Info

Publication number: WO2007080623A1
Application number: PCT/IT2007/000023
Authority: WO
Inventors: Flavio Pantarotto
Original assignee: Flavio Pantarotto
Priority date: 2006-01-16
Filing date: 2007-01-11
Publication date: 2007-07-19
Also published as: ITPN20060003A1; WO2007080623B1

Abstract

A kinematic chain is adapted to translate the alternated linear movement of a linear element into a rotary movement of a shaft or viceversa through a new device which is characterized by at least two cams (1, 2) and (3, 4), each one of which presents a tubular shape, which is provided with contour (6, 7, 8) for a control of at least a cursor (28), whereas transmission means (10-13, 16-19 and 21, 22) are controlling the transmission of a rotary movement to a shaft (14).

Description

KINEMATIC CHAIN OF A MOTOR.

The present invention relates to a kinematic chain, wich is adapted to translate the alternated movement of a linear element into a rotatoty movement of a shaft, or viceversa.

According to prior art, the connecting rod-handle system could be confuted because of a plurality of problems, such as encumbrance of the whole, production costs, as well as complex balancing of the envolving eccentric masses.

It has to be pointed, out that the engineer of whatever machine adopting the connecting rod-handle system is forced to find out difficult compromises, because the construction of such a system often represents a costramt, but at the same time a necessity.

We could consider, for instance, an internal combustion engine, or a pump, or once more a piston compressor: the involved fluid masses inside these ones are obliged to run tortuous routes along wich they must accelerate, stop and invert the movement direction, winning their own inertia, with big energy waste, which causes a low efficiency of them.

The most important constraint of the crankshaft is, anyway, given by the fact that the piston run is always the double of the handle arm, whereby just two variables during engineering exist: swept volume and the relation piston diameter/run.

Consequently, diatneter must be reduced whenever working with considerably long handle arms. Then, with the same swept volume, the smaller the diameter is, the smaller the surface, on which the pressure is working will be, so the lower the obtained force will be..

It should be pointed out that the traditional construction doesn't allow to reach high efficiency.

By short-run engines, where diameter is bigger than run, thermodynamic efficiency reaches better results, but, being handle arm inevitably half of the piston run, the generated torque is small. Therefore, aiming to obtain considerable power, the engine must work at high speed rate.

This requires the extreme lightening of all parts involved in alternated movement and the meticulous balancing of all rotating ones, and consequently the maximum efficacy of lubricating and cooling systems.

The aim of the present invention is to conceive a kinematism, which replaces traditional connecting rod/handle system and which allows to engineer to conceive a piston engine, which overcomes the problems caused by its own construction.

•The following objectives can be reached: 3

2 by exploiting the most part of the pressure produced in the combustion chamber independency of the piston run from the lever arm, which acts on engine shaft, in order to encrease diameter without reducing torque rate; by making linear the gas run from the air box to the exhaust area, in order to exploit rather than to oppose their inertia; by industrializing the engine as an autonomous unity, which allows to obtain different swept volume and power engines coupling in such a way a plurality of cylinders to transmission mechanisms, in order to reduce the production costs (modulus solution); by realizing a structure which, coupling mechanic and electric parts, makes possible an alternated feeding either with fuel or electricity according to requirements.

Such a result could be obtained by the kinematic chain according to the invention, which is characterized by at least two rotating bodies, each one of said rotating bodies having a tubular shape, provided with ondulated contours for- the control of at least a cursor, transmission means being provided for the transmission of a rotary movement to a shaft.'

Said and further characteristics will be apparent through the following description and the alleged drawings:

Figs. Ia, Ib represent respectively a whole plant view and a section view taken according lines A-A of the ki^ήematism according to the invention, taken in correspondence of the superior dead point;

Fig. 2 represents a perspective view of the kinematism of Fig. Ia;

Fig. 3 represents a plan view of one of the elements of the kinematism;

Fig. 4 represents a plan view of another element of the kinematism;

Fig. 5 represents a B-B section view of an element of Fig.3;

Fig. 6 represents a (D-C section view of an element of Fig.4;

Fig. 7 represents a perspective view of an element of Figs.3,5;

Fig. 8 represents an¹ perspective view of an element of Figs.4,5;

Figs.9,10 represent respectively a side and a perspective view of the kinematism according to the invention, at the moment of the superior dead point;

Figs.11,12 represent a side and a perspective view of the kinematism according to the invention, taken in correspondence of a 20° rotation of the same one;

Figs.13,14 represent a side and a perspective view of the kinematism according to the invention, taken imti correspondence of a 40° rotation of the same one;

Figs.15, 16 represent a side and a perspective view of the kinematism according to the invention, taken in correspondence of a 60° rotation of the same one;

Figs.17,18 represent a side and a perspective view of the kinematism according to the invention, in correspondence of a 80° rotation of the same one;

Figs.ϊ'9,20 represent a different disposition of the kinematism according to the invention, respectively at the superior and at the inferior dead point;

Fig.21 represents one of the possible applications of the kinematism according to the invention; ^'

Fig.22 represents a further possible application of the kinematism according to the invention

Fig.23 represents a^'view of the application of Fig. 22;

Fig.24 represents the kinematism according to the invention provided with two cursors instead of one, in four different moments of its rotation, each one encreased of 45° towards the preceeding one;

Fig. 25 represents a possible application of the kinematism of Fig. 24.

The kinematic chain according to the invention comprises two couples of coaxial cams, respectively 1,2 (external) and 3,4 (internal) as it will be apparent hereafter (Figs. 5,6,7,8). The coaxial cams are here named as rotating bodies 1,2 and 3,4. When required the external cams 1,2 can be integral with each other, the same happens for the internal cams 3,4 According to such a solution, it is possible to obtain just two rotating bodies.

Said cams 1,2,3,4 have a tubular shape; each one being provided with contours made of crests 6 and valleys 7 connected by inclined ramps 8 .

The inclined ramps 8 belong to two cams, respectively 3,1 or 4,2, wich rotate one inside the other in opposite direction. They form two grooves 9 ( Figs. 13, 14 ). Crown wheels, respectively 10,11,12,13 (Figs. 5,6) are integral with all the cams 1,2,3,4.. As hereafter explained, the crown wheels 10 - 13 are expected to connect each one of the earns 1,2,3,4 to a shaft 14, working with other gear-wheels 16,17,18,19, which are integral with the same shaft 14 (Fig. Ib).

The interposition of two idle gears 21,22 (Figs. Ia, Ib) is provided between the shaft 14 and the internal cams 3,4. The duty of idle gears 21,22 is to grant for the rotating direction inversion of the internal cams 3,4 with respect to the external ones 1,2.

The crown wheels; 10-13, the gear-wheels 16-19 and the idle gears 21,22 represent transmission means' for the transmission of the rotatory movement to a shaft 14.

Rolling tracks, respectively 23 and 24,26, are adapted to lodge conical rollers 27 or similar (Fig. Ib) on the internal surface of the external cams 1,2 and on the external surface of the internal cams 3,4. The rolling tracks 23,24,26, together with the conical rollers 27, allow to avoid every grazing friction between the moving elements.

A cursor 28, provided with pins 29, is running inside the cams 3,4; eight idle rollers 30,31 respectively internal and external, are adapted to roll on said pins 29. As it will be apparent later on, the cursor 28 is adapted to play the function of a piston 32, when it runs in correspondence of the interior of a cylinder 33.

The idle rollers 30,31 are adapted to roll on the contour of the cams 1,2,3,4, thus translating the rotatory movement of said cams into a linear movement of the cursor 28.

A baseplate 34 is provided between the internal cams 3,4, which is adapted to allow the only rotation of cams 1 ,2,3,4 around their axe.

Said idle rollers 3 Op 1 rotating on the pins 29 have a variable section (Fig.lb), in order to make constant the ^'rolling speed on the contours of the cams according to the distance between the contact point and the rotation center.

The kinematic chain according to the invention is working according to the following way: the contours of the cams 1,2,3,4 form four grooves 9 (Figs. 13,14). During the rotation' of the superior cams 1,3 two diametrically-opposed grooves 9 tend to divaricate, thus allowing to the idle rollers 30,31 rolling on the contours of the cams 1,3 to roll down along their ramps 8 (Figs 9-18); at the same time, the grooves 9 formed by the inferior cams 2,4 tend to tighten, thus obliging the idle roller 30,31 rolling on the contours of the cams 2,4 to roll up along their ramps 8; the cursor 28 is obliged to move downwords (Fig.9-18); during the rotation of the cams, the idle rollers 30,31 run along flat sections, coinciding with the crests 6 of a couple of cams 2,4 and with the valleys 7 of the opposed couple of cams 1,3; said flat sections allow to cursor 28 to remain stationary while the cams continue to rotate, for a time wich will be variable or reducible to zero, depending on the adopted utilization of the kinematic chain according to the invention; just after overcoming the said inferior flat section, during the rotation of the superior cams 1,3 two diametrically-opposed grooves 9 tend to tighten, thus obliging the idle rollers 30,31 rolling on the contours of the cams 1,3 to roll upwords along their ramps 8 ( Fig. 9

- 18 ); at the same time, the grooves 9 formed by the inferior cams 2,4 tend to divaricate, thus allowing the idle rollers 30,31 rolling on the contours of the cams 2,4 to roll down along their ramps ^'8; the cursor 28 is obliged to move upwords. At the end of this run there will be a superior flat section, the same as the already described inferior one; at this point, the cams 1,2,3,4 have covered half a rotation, the cursor 28 has performed a whole cycle and everything can start again,

It has to be pointed out that said kinematic chain can work in both cases when the cams 1,2,3,4 will oblige the cursor 28 to move and when the cursor 28 will oblige the cams 1,2,3,4 to rotate.

Of course, an engineering process of the elements in proper way allows to insert inside the cams two perpendicularly placed cursors, wich are adapted to always move at the same but opposed speed, thus completely exploit the potential of the kinematism.

Consequently, the operative application of the kinematic chain according to the invention is adapted to follow different ways:

- the way of a two or four strokes internal combustion engine;

- the way of a pump;

- the way of a compressor;

- the substitution of ' the connecting rod-handle system, wherever it is possible and advantageous (steam powered machines, textile and sewing machines, vibration generators and so oh).

The advantages, wich can be applied to the different ways, consequently to the application of the idea up to now described, are a plurality among wich:

- a different architecture with consequent optimal occupation of volumes, dimension and shapes, resulting granted by X cursor traslation axe (Fig. Ib) coinciding with cams rotating axe;

- a quite rational disposition of auxiliary mechanic components (timing system);

- a substantially flexible definition of connection between rotary and linear movement, with consequent large optimization possibility: a) of intake, compression, expansion and exhaust cycles; b) of piston diameter/run relation; c) of piston acceleration and maximum speed during working time;

- a substantially absolute and easy possibility to couple several similar and independent unities, in order to enlarge swept volume and power requirements, thus reducing the costs of every unity thanks to big production volumes. Application of the kinematic chain according to the invention to an intt engine

As far as such application is concerned, the connecting rod-handle system elimination allows to substantially compact the whole, practically reducing the engine to a cylindric shape development (Fig.21), where the engine shaft rotation is coinciding with piston 32 axe, said piston being connected with the cursor 28 end.

As for the gases run, the intaken air runs along a substantially linear run, starting from the air box through the hollow cursor 28 up to the combustion chamber, and his own inert_ia makes easier the cylinder filling, as during the irnmission phase, the piston moves opposite the air, going towards it instead of obliging it to follow itself like in traditional engines.

The cursor end, wich is opposite to the combustion chamber, is adapted to follow the compressor function, exploiting the pressure that normally is produced inside the carter when the piston gets in it (Fig.21).

Such a pressure is defined "parasitical" in a traditional four strokes engine, because it opposes the piston movement. When the kinematism according to the invention is applied, said pressure is transferred to the intaking area, increasing engine performances without using any additional devices (turbines, etc.).

As for disposition of auxiliary mechanical components, the timing controls can be placed inside base cylindric structure, with consequent possibility to eliminate the substantially complex and cumbersome typical disposition of traditional engine.

The cylindric structure, with its coaxially rotating elements, allows the location of a stator system (baseplate and cylinder whole 33,34 ) and a rotor (on the external cams 1,2), with consequent possibility of the internal combustion engine integration with electric components like starter and generator.

Furthermore, it's possible to define according to a substantially correct way the piston movements during combustion obtaining its optimization, in order to encrease engine efficiency and decreasing polluting emissions.

All this due to the fact that the piston movement is defined by the cam contour difference in height between crests and valleys, where as the lever arm producing the engine torque is just determined by the medium diameter D (Fig. 1 a) of said cams.

This is one of the most important advantages of the kinematism according to the invention, wich offers to an engine designer a third variable (cam diameter), wich is independent from usual ones (piston diameter and run).

The best efficiency research possibility is practically enlarged.

The same happens for mechanical efficiency of the kinematism, wich receives the linear thrust of the piston 32 on two diametrically opposed points of every cams; then it translates it into a torque, avoiding to waste it on the rotation fulcrum as it happens in a crankshaft traditional engine.

The presence of 'the flat sections in cams 1,2,3,4 contours in corrispondence of the superior and inferior dead points, ensures the possibility to delay any phase beginning for the previous phase optimization.

At the end of the intake run, the piston 32 "waits" with open inlet-valves that the volume of the cylinder had been completely filled by fresh air. After ignition, the piston 32 delays the expansion run beginning, as long as the pressure in the combustion chamber reached the highest rate, also reducing to 0° the spark lead. The exhaust-valves can be opened whⁱle the pⁱston statⁱons at the inferior dead point, discharging residual pressure before the beginning of the exhaust run.

The application of the kinematism according to the invention allows also to fit in the same cylinder two opposed pistons 32, thus obtaining a single high-efficiency combustion chamber (Figs. 22,23).

Consequenlty, it is possible to achieve a substantial simplification with respect to the traditional architecture of a similar motor, adopting two crankshafts.

Application of the kinematic chain according to the invention to a compressor or to a pump

It has to be- pointed out that all the up to now described peculiarity will bring their positive effects also using the kinematism to control the pistons of a compressor or of any type of fluids high-pressure pump.

The kinematism according to the invention, in facts, translates a rotary movement into a linear alternate movement granting the absolute unidirectionality of the treated fluid (the same if it's air-fuel mix, water or any type of fluid), at least the property to put in motion every fluid never forcing it to change direction. This grants substancial advantages in terms of productive work/absorbed energy relation.

In facts, the treated fluid inertia can be exploited rather than opposed, avoiding a consistant energy waste. Thus obtained thanks to the cursor 28, wich acts as intaking or exhaust duct, like already cleared out in the internal combustion engine description.

In the case it's n©t necessary to privilege the fluid speed inside the pump, but the objective to reach is the biggest flow, the kinematism according to the invention can be configurated in the shape shown in Fig. 24.

Said figure illustrates the kinematism provided with two cursors 28 instead of one, in four different moments of its rotation, each one increased of 45° towards the preceeding one. It is apparent that this configuration multiplies the advantages offered by the application of the kinematism according to the invention towards the crankshaft, when it works with two pistons.

Therefore this shape is substantially adapted to the realization of pumps and compressors, in wich the cams 1,2,3,4 can be equipped with rotoric coils, realizing the electric motor wich gives the necessary rotation to the same cams.

However, the same configuration can be applied to the internal combustion engines with traditional overhead valves timing system (Fig. 25).

Further production schemes relating to internal combustion engine are known, particularly the US. patents No.3 ,475,887, No.5,551,383 and the U.S. patent application No.2004/0231620 A1.

Said patent papers are based oin a rotating body, whose ondulated profile guides cursors according to an alternated linear movement. This is an innovative principle of sure interest, as well as drawback that they can't, find such a solution, which guarantees a substantially satis&cting kinematic efficiency.

Said patent document present a main weak point, represented by the using of a single rotating body relating to each cursor. This requires the presence of a support point, which forbids the cursor to rotate. This causes the waiste on the main frame (basement) of most energy transmitted between rotating body and cursor, exactly how it happens between a crankshaft and its main bearings. In addition, the cutting strength applied on pins obliges their overdimension, increasing in such a way the alternated movement loads. Therefore, it is apparent that the innovation of the kinematism according to the invention substantially consists in the using, for each cursor, of at least two rotating bodies, moving in opposite direction.

Such a solution allows no waiste of the reaction strength, which unavoidably is produced by trannformation of a linear strength into rotating torque, and to transfer said reaction strength to the transmission means or viceversa.

Such a factor results already enough to overcome further inventions on kinematic efficiency plan.

A further advantage limited to the kinematism according to the invention, is represented by the hollow cursor, which is adapted to act as intaking or exhaust duct, avoiding to involve the area where mechanical devices are lodged.

Claims

1. Kinematic chain adapted to translate the alternated linear movement of a linear element into a rotary movement of a shaft, or viceversa, characterized by at least two rotating bodies (1,2) and (3,4), each one of said rotating bodies having a tubular shape, said rotating bodies being provided with ondulated contours (6,7,8) for the control of at least a cursor (28), transmission means (10,11,12,13,16,17,18,19,21,22) being provided for the transmission of a rotary movement to a shaft (14).

2. Kinematic chain according to Claim 1, characterized in that crown wheels (10,11,12,13), gear-wheels (16,17,18,19) and idle gears (21,22) represent transmission means for the transmission of the rotatory movement to the shaft 14

3. Kinematic chain according to Claim 1, characterized by crown wheels (10,11,12,13), which are adapted to connect each one of rotating bodies (1,2), (3,4) to a shaft (14), which is working with other gear wheels (16,17,18,19), said gear wheels resulting integral with said shaft (14).

4. Kinematic chain according to Claim 1,2, characterized by at least two pins (29), said pins (29) being integral to the cursor (28), which is called to play the function of a piston (32), when it is running in correspondence of the interior of a cylinder, whereas a plurality of idle rollers (30,31), respectively internal and external, are adapted to roll on contours made of crest (6) and valleys (7), connected by inclined ramps (8) of said rotating bodies (1,2), (3,4)

5. Kinematic chain according to Claims 1,2, characterized in that axe (X) of the cursor (28) translation is substantially coinciding with rotating axe of said two rotating bodies (1,2),(3,4), obtaining in such a way a consequent optimal occupation of volumes, dimensions and shapes of kinematic chain, as well as the runs of cursor (28) is depending on difference of height of rotating bodies contours (6,7,8), whereas the lever arm which determines produced or absorbed torque is only due to medium diameter (D) of rotating bodies (1,2,3,4).

6. Kinematic chain according to Claims 1,2,3, characterized in that the industrial application of said kinematic is adapted to be extended to an internal combustion engine or to a comprimed gas motor or to any type of high pressure fluid pump or gas compressor.