WO2009007474A1

WO2009007474A1 - Rotary piston and cylinder drive system

Info

Publication number: WO2009007474A1
Application number: PCT/ES2008/000237
Authority: WO
Inventors: José Antonio PÉREZ RAYO
Original assignee: Perez Rayo Jose Antonio
Priority date: 2007-07-09
Filing date: 2008-04-14
Publication date: 2009-01-15
Also published as: ES2291142A1; ES2291142B1

Abstract

The invention relates to a rotary piston and cylinder drive system (Fig. 1) formed by a piston (8) and a cylinder (1) which move jointly in a circular manner, in which the force of the combustion in the compression chamber (4) of the cylinder rotates same, the movement thereof being transmitted by a shaft (2). The piston (8) moves in a circular manner about a stationary shaft (16) eccentric to the above-mentioned shaft (2), thereby providing the variation in volume necessary for the compression of the gases in the compression chamber (4). The invention can be used as a drive system for four- or two-stroke engines and as a compressor.

Description

ROTATING PISTON AND CYLINDER MOTRtZ SYSTEM

D E S C R I P C I O N OBJECT OF THE INVENTION

The present invention relates, as stated in the statement, to a rotary piston and cylinder driving system that contributes to the function to which a series of advantages and characteristics are destined, apart from others inherent to its organization and constitution, which will be described. in detail later, and that suppose an innovative alternative and / or improvement to what is already known in this field.

More specifically, the object of the invention consists of a volumetric drive system in which the work carries out the expansion of the gases, as a consequence of their combustion in a compression chamber, which act on the moving organs, a cylinder and a piston, cyclically describing a volume that varies between a maximum and a minimum, without dead spots in any motive element during the cycle, and which can function, with small constructive variations, as a motor system for motors four-stroke, two-stroke and as a volumetric compressor.

SCOPE

This invention has its field of application within the industry dedicated to the manufacture of motors and motor systems in general. BACKGROUND OF THE INVENTION

At present and as a reference to the state of the art, it should be mentioned that many types of engines are known.

Jet engines, reactors, are known in which the work is produced by the gases af leaving the spout. Its application is limited to missiles and modern aircraft.

Continuous flow motors in which the pressurized gas flow moves rotors with rotary motion, called turbine engines. Its applications in the car are only experimental, due to the high costs derived from sophisticated manufacturing technology due to the high temperatures in the turbine and the burner, as well as the high rotational speed of the rotor.

Internal combustion engines with reciprocating linear piston, Otto and Diesel, Wankef triangular rotor motor that moves inside an epitrocoidal chamber, the Stirling engine and the free piston engine, from Pescara.

The reciprocating piston engines use a crank-crank system to transform the alternative linear motion into circular motion, so that every 180 ° of rotation of the crankshaft, the piston and the connecting rod enter a neutral position to change the direction of their movement with the consequent absorption of energy.

In the triangular rotor, called Wankel, the rotor transmits its movement to a main axis through a gear, the said rotor moving on an epitrocoidal chamber of complex manufacture and that does not resolve, totally, the absorption of energy by the rotor. Pescara's free piston engine has had no relevant industrial application.

The Stirling engine obtains mechanical power from the expansion of a gas locked at high temperature, using two chambers and an external burner; it was used as a small power source in many industries during e! 19th century and early 20th century.

In the aforementioned systems, the mechanical components are numerous and of complex shapes and the parts that convert the movement into rotary, absorb a considerable part of the power developed by the system, subtracting it from the useful power.

It is worth mentioning, that e! The petitioner is unaware of the existence of a rotary piston and cylinder drive system that has similar technical, structural and constitutive characteristics to those of the present invention, which aims to solve the aforementioned drawbacks presented by the systems currently known for the same finish.

EXPLANATION OF THE INVENTION

The rotary piston and cylinder drive system proposed by the invention constitutes, by itself, an obvious novelty within its field of application, since from its application, a considerable reduction in manufacturing complexity is thus achieved as the number of components thereof, such as cylinder bed, gears, crankshaft and balancing weights, on the other hand obtaining a greater use of engine power. The main innovation of the driving system of the invention, with respect to the current internal combustion engines, is the elimination of the crankshaft, dead spots, the simplification of construction, the regularity of operation and the absence of vibrations.

Thus, the piece that receives and transmits the force of combustion, performs a circular motion; This piece is a rotating cylinder, with a compression chamber where the piston slides. The center of rotation of the cylinder is, in turn, the transmission shaft.

The piston rotates, dragged by the cylinder, around an eccentric axis to that of the cylinder, and only performs circular motion. By rotating the cylinder and piston together, the volume variation necessary to compress the gases in the compression chamber of the cylinder is achieved.

Thanks to its structure, the invention simplifies, notably, the number of parts compared to those that are necessary for the operation in the driving systems of the current internal combustion engines.

On the other hand, as mentioned above, and by means of the realization of small constructive variations, it should be noted that the system of the invention allows a variant of embodiment, as a driving system for four-stroke engines, a variant of embodiment as a driving system for two-stroke engines and a variant embodiment as a volumetric compressor.

The intake and exhaust systems will be formed by plates that move over the periphery and can be operated mechanically, electrically, hydraulically, etc. The feeding can be done by carburation or by injection, being valid (os current systems.

Lubrication is preferably carried out by means of the system called "forced lubrication".

For the cooling of the system, a mixed air-oil system, or water-oil will be used.

The tightness of! piston in the cylinder and the tightness of the compression chamber, is performed by incorporating segments that are placed in the piston and in the periphery of the cylinder.

Finally, the ignition, for gasoline engines will be done by conventional electronic ignition systems, and for gas-oil engines, the ignition will be done by compression.

The new rotary piston and cylinder drive system therefore represents an innovative structure with structural and constitutive characteristics unknown until now for such purpose, reasons that, together with its practical utility, provide it with a sufficient foundation to obtain the privilege of exclusivity request.

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 descriptive report is attached, as an integral part thereof, of a set of drawings, in which with character Illustrative and not limiting, the following has been represented: Figure number 1.- Shows an exploded perspective view of the elements that form the driving assembly of the invention.

Figures number 2 to 9.- They show respective views in plan and in section according to a longitudinal section of the system in its different operating phases in its variant embodiment as a four-stroke internal combustion engine, showing each of said views respectively. rotation rod at 0 ^or 90 °, 180 °, 270 °, 360 °, 450 °, 540 ° and 630 °.

Figure number 10.- Shows a perspective and sectional view according to a cross-section of the system of the invention according to the same variant represented in figures 2 to 9, enlarging the spatial vision of said figures corresponding to the operating phases as an engine of four times and improving the understanding of the operation of the driving system, as well as illustrating, once assembled, the parts that constitute itself.

Figure 11 shows a perspective and exploded view of the system of the invention in its variant embodiment as a two-stroke engine.

Figures number 12 to 15.- They show respective views in plan and in section according to a longitudinal section corresponding to the different phases of operation of a variant of embodiment of the system of the invention represented in Figure 11, as an internal combustion engine of two times, respectively showing each of said views the rotation of the connecting rod at 0 °, 90 °, 180 °, 270 °.

Figure number 16.- Shows a perspective and 90 ° sectional view of the two-stroke engine assembly shown in Figures 12 to 15. Figure number 17.- Shows a perspective and sectional view at 90 ° of the system of the invention in its variant embodiment as a volumetric compressor.

Figures number 18 to 21.- They show respectively views in plan and in longitudinal section, relative to the different phases of operation of the system, in its variant embodiment as a volumetric compressor represented in figure 17, showing each one of said views respectively and! rotation of the rod at 0 ^or 90 °, 180 °, 270 °.

PREFERRED EMBODIMENT OF THE INVENTION

In view of the mentioned figures and according to the numbering adopted, an example of a preferred embodiment of the rotary piston and cylinder drive system comprising the parts indicated and described below can be observed.

Thus, as can be seen in Figure 1, the driving system consists essentially of:

Ef cylinder (1) comprising, forming the same piece:

- The drive shaft (2), to which a flywheel will be assembled, not shown.

- The gas compression chamber (4).

- The chamber (4bis), where the circular path of the connecting rod (7) is carried out, and which will also serve as a gas precompression chamber, in the case of a two-stroke engine application.

- The housings (5) for segments (3) and (15).

- The accommodation (5bis) for the segment (6). The enveloping cover (11), which in turn comprises:

- The housing (14} of the intake valve (13) - The housing (10) of the exhaust valve (9).

- The hole (12) for the corresponding spark plug, in the case of being used as an Otto cycle engine, or for the corresponding fuel injector in case of operation as a Diesel cycle engine.

- The output hole (19) of the transmission shaft (shown in Figure 10).

- The connecting rod (7).

- The piston (8).

The side cover (17), comprising:

- The pipe hole (18) through which lubrication fluids will be introduced, when it functions as a four-stroke engine.

- The eccentric support or shaft (16) of the connecting rod (7).

The covers (11) and (17) incorporate respective supports and conventional anchors for their coupling not shown.

In this way, for the realization of the cycle, the piston (8) and the cylinder (1) perform a circular movement, in a solidary manner, dragging the cylinder to the piston.

The force of combustion exerted on the compression chamber (4) of the cylinder (1) rotates it, transmitting its movement along the axis (2).

The piston (8), dragged by the cylinder (1), performs a circular movement, around a fixed axis (16) eccentric to the axis (2) of the cylinder (1), supported, through the connecting rod (7), on said axis (16); With this movement, the volume variation necessary for the compression of the gases in the compression chamber (4) is achieved.

In one embodiment, the invention can function as a four-stroke internal combustion engine, whose operating phases, represented in Figures 2 to 9, are:

Admission. Start-up is carried out using the traditional starter and gear crown system on flywheel (not shown) that is assembled with the drive shaft (2).

The piston (8) and the cylinder (1) are in the position of 0 ^or , (figure 2) and minimum volume in the compression chamber (4).

When the rotation begins, the intake valve (13) opens and the combustible fluid, coming from the corresponding intake manifold, begins to fill the compression chamber (4), absorbed by the vacuum caused by the movement of the piston (8) , (figure 3), and remains open until the position of maximum volume, which occurs when a 180 ° rotation has been made (figure 4). In this position the compression chamber (4) has been filled and the intake valve (13) is closed. The rotation of the admission phase has been 180 °.

The actuation of the intake valve (13) can be carried out by means of a mechanical or electrical system, synchronized with the rotation of the cylinder (1).

As feed, injection or carburetion system, any of the existing ones can be used. Compression. The compression phase begins from the 180 ° rotation position (figure 4), the volume in the compression chamber (4) being progressively reduced and the gases being compressed. This position, (figure 5), represents the cylinder (1) and piston (8) in the middle of the compression phase, which ends in the 360 ° rotation position (figure 6), in which the volume in the Compression chamber (4) is minimal, and the gases are compressed to maximum.

Job. It begins in the 360 ° rotation position, (figure 6), with the ignition of the mixture in the compression chamber, either by the spark jump of a spark plug, case of application as Otto cycle engine, or by ignition by compression, with Sa corresponding fuel injection, application case as a diesel cycle engine.

Upon entering the combustion mixture, the thrust of

The expansion of the gases on the cylinder (1), thus carrying out the working time. The thrust made on the cylinder by the expansion of the gases during combustion, is reduced as the compression chamber (4) increases in volume. The position of 450 ° of rotation (figure 7), represents the cylinder (1) and piston (8) in the middle of the working stroke, which ends in the position of 540 ° of rotation, (figure 8).

Escape. In ϊa position of 540 °, (figure 8), the gas evacuation phase begins, with the opening of the exhaust valve (9). The 630 ° rotation position (figure 9) represents the cylinder (1) and piston (8) in the middle of the escape time course, in which the volume in the compression chamber (4) is progressively reduced. , until the total evacuation of the gases with which the cycle ends closing the exhaust valve (9) (figure 2).

The duty cycle has been performed during 720 ° of rotation. Ef actuation of [to exhaust valve (9), can be performed by a mechanical or electrical system, synchronized with the rotation of the cylinder (1).

The driving system, in one embodiment as a two-stroke internal combustion engine, is basically the same, eliminating the intake (13) and exhaust valves (9) and their respective housings (14) and (10) as It can be seen in the exploded view of Figure 11. In the cylinder (1) an exhaust nozzle (20) has been made, and in the skirt of the compression chamber (4), a gas transfer channel ( 21), as seen in Figure 12. Through the orifice of pipes (18) the fuel fluid is fed into the precompression chamber (4-bis).

The phases of its operation, represented in the figures

12 to 15, are:

Work-precompression. In Sa position of 0 ^or (figure 12), the compression chamber (4) is filled with compressed fuel gas, so that when it goes into ignition (by spark jump, in case of application to Otto cycle engine, or by fuel injection, in case of application to the cycle engine Say [), the expansion of the gases occurs, exerting its force on the cylinder (1) during the rotation of the same to the position of entry in communication of the chamber ( 4), with the exhaust nozzle (20) (figure 14). Likewise, the chamber (4bis) is filled with combustible gas, so that the reduction in volume in said chamber (4bis), produced by the piston (8) in the rotation of 0 ^or 180 °, will reduce the volume of The aforementioned chamber (4bis) performing a precompression of the existing gases therein.

The 90 ° rotation position (figure 13), represents the precompression work time, in the middle of the path, when the force exerted on the cylinder has been reduced considerably, by increasing the volume in the compression chamber (4).

Admission-escape. A few degrees of rotation before the 180 ° position (figure 14), (depending on the advance to the intake and the exhaust respectively), the pre-compression chamber (4bis), is put in communication with the compression chamber (4), through the transfer channel (21), and the pre-compressed gases pass from the chamber (4bis) to the chamber (4), pushing the burned gases (20) towards the exhaust nozzle and filling the compression chamber (4).

Compression-preadmission. A few degrees of rotation after the 180 ° position (figure 14), (depending on the delay to the admission and the exhaust respectively), simultaneously begin the compression of the gases in the chamber (4) and, at through the orifice of pipes (18), the supply of combustible fluid, called pre-admission, to the pre-compression chamber (4bis).

In the position of rotation of 270 ° (figure 15), the preadmission is at its midpoint and ends at the position of 0 ^or (figure 12), in which a new cycle begins with the ignition of the gases .

The duty cycle was carried out during 360 ° of rotation of the cylinder (1).

Any of the currently existing injection or carburetion systems can be used as the feeding system.

Finally, in figure 17 an embodiment of the driving system of the invention is observed as a volumetric compressor, which is also basically the same, eliminating also [as intake valves (13) and exhaust exhaust (9) and their respective housings (14) and (10) and incorporating the nozzle (20), which allows the entry of gas, and which is connected to the pipeline (22), practiced on the inner face of the enveloping cover (11), and whose operating phases, represented in figures 18 to 21, are:

The mechanical drive is carried out through the transmission shaft (2).

Admission. It begins when the compression chamber (4) communicates with the pipeline (22), which in turn is communicated with

The gas inlet (20). This occurs a few degrees of rotation after

The position of minimum volume (figure 18), and continues until the position of maximum volume in the compression chamber (4) (figure 20).

The gas inlet is produced by the pressure created in the compression chamber (4), by the movement of the piston (8).

The 90 ° position (figure 19) represents the admission phase at the midpoint of its travel.

Compression. It begins a few degrees of rotation after the 180 ° position (figure 20), when the compression chamber (4), already filled with gas, ceases to be communicated with the air inlet (20). From that moment the volume reduction in the compression chamber (4) begins, and the consequent compression of the gas to the 0 ^or position (figure 18), in which the pressurized gas is expelled through the outlet orifice (12), equipped with a check valve, and a new cycle begins.

The 270 ° position (figure 21) represents the compression phase at its midpoint. Described sufficiently the nature of the present invention, as well as the way of putting it into practice, it is stated that, within its essentiality, it may be carried out in other embodiments that differ in detail from that indicated by way of example , and to which will also reach the protection that is sought as long as it does not alter, change or modify its fundamental principle.

Claims

RE t V t ND l CAC t ONES

1.- ROTARY PISTON AND CYLINDER MOTOR SYSTEM, of volumetric type applicable to internal combustion engines in which the work carries out the expansion of the gases, as a consequence of the combustion thereof in a compression chamber, characterized by the made up of a cylinder (1) comprising, forming the same part, a transmission shaft (2), to which a flywheel will be assembled, a gas compression chamber (4), a chamber (4bis) , where the circular path of the connecting rod (7), housings (5) for the segments (3) and (15), and a housing (5bis) for the segment (6); an enveloping cover (11), which in turn comprises a housing (14) of the intake valve (13), a housing (10) of the exhaust valve (9), a hole (12) for the spark plug or for the fuel injector, a bore (19) of the transmission shaft output a connecting rod (7) and a piston (8); and a side cover (17), which comprises an orifice of pipes (18) and an eccentric support or shaft (16) of the connecting rod (7); in which the cylinder (1), which receives and transmits the force, performs a rotary movement, whose center of rotation is the transmission axis (2); in which the piston (8) rotates dragged by the cylinder (1) around an eccentric shaft (16) ai üe \ cylinder (1), and only performs a circular motion, achieving the volume variation necessary for the compression of the gases in the compression chamber (4).

2.- PISTON AND CYLINDER MOTRfZ SYSTEM

ROTARY, according to claim 1, characterized in that it can function as a driving system for four-stroke internal combustion engine.

3.- PISTON AND CYLINDER MOTRfZ SYSTEM

ROTARY, according to claim 1, characterized in that in another embodiment, eliminating the intake valves (13) and exhaust (9) and their respective housings (14) and (10), practicing an exhaust nozzle (20) in the cylinder (1) and opening a gas transfer channel (21) in the skirt of the compression chamber (4), can function as a driving system for two-stroke internal combustion engine.

4.- MOTOR SYSTEM OF ROTARY PfSTON AND CYLINDER, according to claim 1, characterized in that in another embodiment, eliminating the intake valves (13) and exhaust (9) and their respective housings (14) and ( 10), practicing a nozzle (20) in the cylinder (1) and practicing, in the inner face of the enclosure cover (11), a pipe (22) communicated with said nozzle (20), can function as a volumetric compressor.