ITRM20100507A1 - ROTARY COMPRESSION OR PUMPING DEVICE, AND MOTOR DEVICES USING THIS COMPRESSION OR PUMPING DEVICE. - Google Patents

Description

Rotary compression or pumping device, and motor devices utilizing such compression or pumping device

The present invention relates to a rotary compression or pumping device, and motor devices using such a compression or pumping device.

More precisely, the present invention relates to a compression or pumping device which allows a reduction in external dimensions with respect to existing products with the same displacement characteristics, with an optimized volumetric flow rate and absence of vibrations during operation.

Volumetric compressors are known. However, these have the disadvantage of producing unwanted pulsations in the storage plant and of generating mechanical stresses during operation due to the linear or eccentric movement of the piston. Furthermore, they do not allow the simultaneous use of two different fluids in the machine.

The object of the present invention is to optimize the energy conversion efficiency with respect to existing machines, providing a compression or pumping device that solves the problems and overcomes the drawbacks of the prior art.

A further specific purpose of the present invention is the use of the compression or pumping device which is the object of the invention as an engine.

A further specific object of the present invention is to provide a motor device, comprising the rotary compression or pumping device which is the object of the invention.

A further specific object of the present invention is to provide an exothermic closed loop motor device, comprising the rotary compression or pumping device which is the object of the invention.

The object of the present invention is a rotary compression or pumping device, characterized in that it comprises:

- an external stator with a cavity at the center of which it is axially positioned

- an internal stator,

between the external stator and the internal stator being coaxially arranged in a rotatable way:

- a rotor with crown section, which is kept in rotation by a

- external motor,

and in which:

- the shape of the external surface of the internal stator corresponds to that of the internal surface of the external stator, the shape of the rotor with crown section having an ellipticity different from that of the internal stator and of the external stator, so that said rotor with crown section contacts both the internal wall of said cavity of the external stator in two diametrically opposite external points and the external surface of said internal stator respectively in two diametrically opposite internal points,

- the external stator comprises in diametrically opposite positions a first and a second resilient element arranged on the same plane or otherwise curvilinear and extended in the direction of the axis of the internal stator and which continuously contact the external surface of said rotor with crown section, said first and second resilient element being respectively movable in two opposite directions or opposite rotations between a first position flush with the internal wall of said cavity and a second elongation position inside said cavity, on one side and on the other of said first and second resilient element 2 or 4 corresponding chambers being formed each time;

- the internal stator comprises in diametrically opposite positions a first and a second further resilient element arranged on the same further plane or otherwise curvilinear and extended in the direction of the axis of the internal stator and which continuously contact the internal surface of said crown rotor in two or more respective lines, said first and second further resilient element being respectively movable in two opposite directions or opposite rotations between a first position flush with the external surface of said internal stator and a second elongation position beyond said external surface of said internal stator , on one side and on the other of said first and second further resilient element further corresponding chambers being formed from time to time;

the compressor further comprising:

- in correspondence with the first resilient element, on one side of said plane, a first external port for the passage of the fluid connected to said cavity through a relative series of ducts of first external port, on the opposite side of said plane, a second external port of passage of the fluid connected to said cavity through a relative series of second external port ducts; as well as, in correspondence with said second resilient element, on said opposite side of said plane, a third external port for the passage of the fluid connected to said cavity through a relative series of third external port ducts, on said side of said plane, a fourth external port for the passage of the fluid contained in said corresponding chambers, connected to said cavity through a relative series of fourth external port ducts;

- in correspondence with the first further resilient element, on one side of said further plane, a first internal port for the passage of the fluid connected to said cavity through a relative series of ducts of first internal port, on the opposite side of said further plane, a second internal fluid passage port connected to said cavity through a relative series of second internal port ducts, and in correspondence with said second further resilient element, on said opposite side of said further plane, a third internal fluid passage port connected to said cavity through a relative series of third internal port ducts, on the side of said further plane, a fourth internal port for the passage of the fluid contained in said corresponding chambers, connected to said cavity through a relative series of fourth internal port ducts,

the fluid being aspirated from time to time through two internal ports and two external ports and being evacuated through the remaining two internal ports and two external ports as a consequence of the thrusts exerted on the fluid between said crown rotor and said internal and external stator and said elements resilient.

Preferably according to the invention, said internal and external stator have cylindrical facing surfaces, and said crown rotor has an elliptical crown.

Preferably according to the invention, said plane coincides with said further plane.

Preferably according to the invention, when the rotor is able to turn clockwise, observed in the front position of the lights, said second external light, fourth external light, second internal light and fourth internal light are provided with non-return valves, so that © the compressed fluid does not reverse the direction of flow, and by the fact that the fourth external port and the second external port are connected by means of suitably sized hollow ducts to the first internal port and the third internal port, while, with the anticlockwise direction of rotation of the rotor, observing it in front of the lights, is characterized by the fact that: said first external light, third external light, first internal light and third internal light are equipped with non-return valves, so that the compressed fluid does not reverse the sliding direction, and from the fact that the first external light and the third external light are connected by means of suitably sized cable ducts to the second from inner light and to the fourth inner light.

Preferably according to the invention, said plane is transversal to said further plane.

Preferably according to the invention, with the clockwise direction of rotation of the rotor:

- said second external port, fourth external port, second internal port and fourth internal port are provided with non-return valves, so that the compressed fluid does not reverse the direction of flow;

- said fourth external port and said second external port are respectively connected, with suitably sized hollow ducts, to said first internal port and to said third internal port;

with the counterclockwise rotation of the rotor:

- said first external port, third external port, first internal port and third internal port are provided with non-return valves, so that the compressed fluid does not reverse the flow direction;

- said first external port and said third external port are respectively connected, with suitably sized hollow ducts, to said second internal port and to said fourth internal port.

A further object of the present invention is the use of the rotary device according to the invention as a motor, characterized by the fact that said rotary device is fed by pressurized fluid through four ports, the pressurized fluid generating a driving torque on the crown rotor and being discharged as a consequence of its motion, through the remaining four lights.

A further object of the present invention is a motor device, comprising the rotary device as defined in claim 3, characterized by the fact that said rotary device is adapted to be fed by pressurized fluid, and by the fact that, when the direction of rotation of the rotor is clockwise observed from the side of the exposed lights:

- the first internal port and the third internal port are adapted to receive the fluid under pressure;

- the fourth internal port and the second internal port are suitable for evacuating the pressurized fluid;

- the fourth internal light and the second internal light are connected through suitable pipes to the first external light and the third external light;

- the fourth external port and the second external port are suitable for evacuating the fluid in compression coming from the first external port and the third external port.

A further object of the present invention is an exothermic closed-cycle motor device, comprising the rotary device as defined by the invention in which a gaseous fluid circulates, connected by hollow ducts to a hot heat exchanger and a cold heat exchanger, characterized by the fact that:

- said internal and external stator have cylindrical facing surfaces, and said crown rotor has an elliptical crown;

â ’four lights are connected to the hot exchanger, the remaining four lights are connected to the cold exchanger, by means of cable ducts;

∠'the gaseous fluid flows from the hot exchanger at pressure p' to the cold one, passing through the chambers external to the rotor thus causing its movement, the motion of the crown rotor causing the flow of fluid from the cold to the hot exchanger, which passes through its internal chambers.

A further object of the present invention is the use of the motor device according to the invention as a cryogenic machine, characterized by the fact of applying a driving torque to the crown rotor to create a temperature difference between the heat exchangers.

A further object of the present invention is an exothermic closed cycle motor device, characterized in that it comprises a first sector and a second rotary sector, with respective elliptical ring rotors each as defined by the invention, and in which a fluid circulates carrier gas, the first sector being connected by hollow ducts to a cold heat exchanger and the second device connected by hollow ducts to a hot heat exchanger, said first and second sectors being integrally arranged coaxially with an intermediate separation element, so that the rotors and are free to rotate integrally with the shaft, the planes of the respective resilient elements and the relative rotors and of the first sector and of the second sector being respectively displaced in position by an angle of 90 °,

and by the fact that:

- the sum of the volumes of said corresponding chambers of the second sector is greater than the sum of the volumes of the relative chambers of the first sector, their correct sizing is a necessary condition for the correct functioning of the machine at full capacity;

- four ports of the first device are connected by hollow ducts to the hot exchanger, the remaining four ports of the first device are connected to the cold exchanger, by means of suitably sized cable ducts;

- four ports of the second device are connected to the hot exchanger, the remaining four ports are connected to the cold exchanger, by means of suitably sized cable ducts;

- the hot exchanger is powered by a hot thermal source;

∠’the cold exchanger is cooled by the cold heat source;

∠’the gaseous fluid flows from the hot to the cold exchanger passing through the device chambers and flows to the cold exchanger Sc from the hot exchanger passing through the device chambers, generating the rotary movement of the shaft.

A further object of the present invention is the use of the motor device just described as a cryogenic machine, characterized by the fact of applying a driving torque to said shaft to generate a temperature difference between the heat exchangers.

The invention will now be described for illustrative but not limitative purposes, with particular reference to the drawings of the attached figures, in which: - figure 1 shows the first phase of the operation of an embodiment according to the invention (compressor configuration / pump 1);

Figure 2 shows the second phase of the operation of an embodiment according to the invention (compressor / pump configuration 1);

Figure 3 shows the third phase of the operation of an embodiment according to the invention (compressor / pump configuration 1);

Figure 4 shows the fourth phase of the operation of an embodiment according to the invention (compressor / pump configuration 1);

figure 5 shows the fifth phase of the operation of an embodiment according to the invention (compressor / pump configuration 1);

figure 6 shows the first phase of the operation of an embodiment according to the invention (compressor configuration 2);

Figure 7 shows the second phase of the operation of an embodiment according to the invention (compressor configuration 2);

figure 8 shows the third phase of the operation of an embodiment according to the invention (compressor configuration 2);

Figure 9 shows the fourth phase of the operation of an embodiment according to the invention (compressor configuration 2);

Figure 10 shows the fifth phase of the operation of an embodiment according to the invention (compressor configuration 2);

Figure 11 shows the first phase of the operation of an embodiment according to the invention (compressor configuration 3);

- figure 12 shows the second phase of the operation of an embodiment according to the invention (compressor configuration 3);

Figure 13 shows the third phase of the operation of an embodiment according to the invention (compressor configuration 3);

Figure 14 shows the fourth phase of the operation of an embodiment according to the invention (compressor configuration 3);

figure 15 shows the fifth phase of the operation of an embodiment according to the invention (compressor configuration 3);

Figure 16 shows the first phase of the operation of an embodiment according to the invention (configuration of pneumatic or liquid-fed motor 1);

Figure 17 shows the second phase of the operation of an embodiment according to the invention (configuration of pneumatic or liquid-fed motor 1);

Figure 18 shows the third phase of the operation of an embodiment according to the invention (configuration of pneumatic or liquid-fed motor 1);

Figure 19 shows the fourth phase of the operation of an embodiment according to the invention (configuration of pneumatic or liquid-fed motor 1);

Figure 20 shows the fifth phase of the operation of an embodiment according to the invention (configuration of pneumatic or liquid-fed motor 1);

Figure 21 shows the first phase of the operation of an embodiment according to the invention (configuration of pneumatic motor 2);

Figure 22 shows the second phase of the operation of an embodiment according to the invention (configuration of pneumatic motor 2);

- figure 23 shows the third phase of the operation of an embodiment according to the invention (configuration of pneumatic motor 2);

Figure 24 shows the fourth phase of the operation of an embodiment according to the invention (configuration of pneumatic motor 2);

Figure 25 shows the fifth phase of the operation of an embodiment according to the invention (configuration of pneumatic motor 2);

- figure 26 shows a further embodiment according to the invention (configuration of an exothermic closed loop engine);

- figure 27 shows a perspective view of the device according to the invention, on the crankshaft side;

- figure 28 shows the internal stator of the device according to the invention, the ducts that allow the inflow and outflow of the fluid from the chambers to the ports are highlighted;

- figure 29 shows an embodiment of the engine according to the invention: in (a) the cold sector seen from the front, in (b) the hot sector seen from the front, the rotor in angular position 0 °;

- figure 30 shows an embodiment of the engine according to the invention: in (a) the cold sector seen from the front, in (b) the hot sector seen from the front, the rotor in an angular position -45 °;

- figure 31 shows an embodiment of the engine according to the invention: in (a) the cold sector seen from the front, in (b) the hot sector seen from the front, the rotor in an angular position -90 °;

- figure 32 shows an embodiment of the engine according to the invention: in (a) the cold sector seen from the front, in (b) the hot sector seen from the front, in an angular position -135 °; ∠’Figure 33 shows a schematic representation of the connection of the heat exchangers with the cold and hot parts of the engine of Figures 29 to 32.

- figure 34 shows a side view of the motor of figures 29-32.

In the following description, reference is often made to a specific direction of rotation of the internal rotor. However, the direction of rotation can be reversed, as better described later in the relevant applications.

In the figures, moreover, the shades of gray dotted white, gray dotted black, black indicate three increasing levels of pressure.

Compressor / pump configuration 1

In the first embodiment, the rotary compressor / pump 100 according to the invention comprises, an internal stator 30 (cylindrical), an external stator 20, an elliptical rotor 10 (cylinder with elliptical crown section) kept in rotation by a couple applied tractor.

Between the internal 30 and external 20 stators and the elliptical rotor 10 6 or 8 chambers are delimited according to the reciprocal position of the components, into which the fluid flows and flows. These chambers are also formed thanks to resilient linear (or curvilinear) contrasting elements 60.61 on the outside and 70.71 on the inside placed in grazing contact with the external and internal surfaces of the rotor.

In this configuration:

- the elliptical rotor 10 is kept in rotation by a mechanical torque applied from the outside;

- the direction of rotation is clockwise, to reverse this direction it will be necessary to change the use of the chambers which from compression sectors will become intake, the intake chambers will become compression, while the ducts and intake ports will become exhaust , the exhaust ducts and ports will become intake;

- the direction of the alternating movement of the resilient elements 60,61 is equivalent to that of the resilient elements 70,71.

In the initial phase represented in figure 1, four chambers 42,41,40,43 are observed which are fed by means of the respective ducts 51â € ™ â € ™, 53â € ™ â € ™, 55â € ™ â € ™, 57â € ™ â € ™ connected to the intake ports 51,53,55,57. Other ducts 52â € ™ â € ™, 54â € ™ â € ™, 56â € ™ â € ™, 58 â € ™ allow the inflow or outflow of the fluid from the internal chambers, they are closed by the position of the rotor 10 and they are connected to the lights 52,54,56,58.

Figure 1 shows a section of the device according to the invention. Figure 27 shows a perspective view of the device, while figure 28 shows the internal stator 30 with the ducts 55â € ™ â € ™, 56â € ™ â € ™, 57â € ™ â € ™, 58â € ™ â € ™ observable in transparency, and the relative lights 55,56,57,58 (closed on the opposite side, not visible in the figure).

The ports 52,54,56,58 can be equipped with non-return valves in order to keep the fluid circulation direction unchanged in the system.

The internal chambers (between the internal stator 30 and the elliptical rotor 10), the lights 55,56,57,58 and the ducts 55â € ™ â € ™, 56â € ™ â € ™, 57â € ™ â € ™, 58â € ™ â € ™ they are closed, thanks to the geometry of the device.

The external chambers (between the external stator 20 and the elliptical rotor 10) of the elliptical rotor suck fluid from the ports 51 and 53. The black external chambers compress / stress the fluid conveying it through the ducts 52â € ™ â € ™, 54â € ™ â € ™ in lights 52 and 54.

During the subsequent phases, described below, the intake and exhaust ports remain the same.

The gaseous fluid will then be aspirated by the ports 51,53,55,57 and compressed / stressed in the external and internal chambers of the rotor from which it will flow from the ports 52,54,56,58.

By suitably varying the geometry of the internal stator cylinder 30, of the external one 20 (section of the chambers or depth of the same), of the rotary cylinder 10, the volumes of the chambers are modified, this allows to obtain a continuous flow of the compressed or pumped fluid, eliminating unpleasant pulsations in the downstream or storage system.

Referring to Figure 2, in a second phase the fluid is sucked into the gray-dotted white chambers through the ports 51,53,55,57. In the black chambers, the compressed / stressed fluid flows out through the ports 52,54,56,58.

Referring to figure 3, in a third phase the chambers external to the elliptical cylinder are closed (again thanks to the geometry of the components), in them the fluid is about to be compressed / stressed. In the chambers in gray speckled white, the fluid is sucked from the lights 55,57. The fluid compressed / stressed in the internal chambers in black flows out of the ports 56,58.

With reference to Figure 4, in a fourth phase the fluid is sucked in the gray dotted white chambers through the ports 51,53,55,57. In the black chambers the fluid is compressed / stressed and discharged from the ports 52,54,56,58.

With reference to figure 5, in a fifth phase the first complete cycle of suction, compression and / or pumping ends, while the rotor has performed a rotation of 180 °. The description restarts as shown in figure 1, thus continuing with the new cycle which will end in the following 180 °.

The advantages of this first configuration are: - reduction of external dimensions compared to existing products with the same displacement characteristics. For a complete 360 ° rotation of the crankshaft, the volumetric flow rate is double compared to the sum of the volumes of the internal and external chambers of the rotor 10. In fact, during the 360 ° rotation of the crankshaft, the aforementioned chambers are filled and consequently emptied twice;

- the four chambers are suitable for use as single compressors / pumps, this allows the simultaneous use of different types of fluids;

- absence of vibrations during operation. The cylinder 10 in the rotation movement is in perfect balance. The parts in linear or curvilinear movement (60,61 and 70,71) perform specular movements. All moving parts therefore do not produce unwanted mechanical stress.

Compressor configuration 2

With reference to figures 6 to 10, the second form of application of the invention is described below, which provides a two-stage compression, thus allowing to decrease the maximum value of the mechanical torque applied for the rotor drive to elliptical crown 10.

In this configuration:

- the elliptical rotor is kept in rotation by a mechanical torque applied from the outside; - the direction of rotation is clockwise, reversing this direction will reverse the use of the chambers which from compression sectors will become intake, the intake chambers will become compression, the ducts and intake ports will become exhaust, while the ducts and exhaust ports will become intake;

- the direction of movement of the resilient elements 60,61 is equivalent to that of the resilient elements 70,71;

- for correct operation, the ports 52,54,56,58 will be equipped with non-return valves, so that the compressed fluid does not reverse the direction of flow in the system;

- ports 52,54 are connected by means of suitably sized hollow tubes to ports 55,57;

- the shades gray dotted white, gray dotted black, black indicate three increasing levels of pressure.

In figure 6, in a first phase the gaseous fluid is sucked by the ports 51,53, flows into the external chambers (gray dotted white), compressed in the gray ones dotted black due to the stress of the cylinder 10, and made to flow through the ports 52 , 54. The ports 52,54, equipped with the aforementioned non-return valves, allow the outflow of the compressed fluid in the hollow pipes connected to the ports 55,57 which in this phase are closed.

With reference to Figure 7, in a second phase the fluid is sucked into the external chambers (in gray dotted white) through the ports 51,53. The fluid flows from the ports 52,54 and has undergone the first pressure gain in the external chambers (gray dotted black) to the rotor 10. The ports 55,57 receive the compressed fluid from the sectors external to the cylinder and flows into the internal chambers (in gray dotted black). Finally, from the ports 56,58, the fluid further compressed in the black chambers flows towards the storage or use plant.

Referring to figure 8, in a third step the external chambers (gray dotted white) are closed, in them the fluid is about to be compressed. In the internal chambers (in gray dotted black) the fluid, coming from the cable ducts connected to the ports 52,54, flows from the ports 55,57 where it is again stressed and subjected to the subsequent pressure increase. From the internal chambers (in black) the fluid flows through the ports 56,58.

With reference to Figure 9, in a fourth step the fluid is sucked in the chambers in gray dotted white through the ports 51,53. From the ports 52,54 of the external chambers (gray dotted black) to the rotor 10, the fluid flows in the cable ducts and flows to the internal chambers (gray dotted black) from the lights 55,57 to be further compressed. In the internal chambers (in black) the fluid undergoes the last pressure gain and flows out of the ports 56,58.

Referring to figure 10, in a fifth phase, while the rotor 10 has performed a rotation of 180 °, the first complete suction / compression cycle ends, in the subsequent rotation of 180 ° a new cycle will continue which will end in the subsequent rotation of 180 °, the descriptions are repeated from figure 6 to figure 10.

The advantages of the second embodiment are:

- greater efficiency in the dissipation of the heat produced in the compression of the fluid; - the use of a maximum mechanical torque applied, useful for driving the lower rotary cylinder 10;

- absence of vibrations, organs in rotational movement in equilibrium, the resilient elements in symmetrical linear motion also in equilibrium.

Compressor configuration 3

With reference to figures 11 to 15, the third form of application of the invention is described below, thus realizing a two-stage compression.

In this configuration:

- the elliptical rotor is kept in rotation by a mechanical torque applied from the outside;

- the direction of rotation is clockwise, to reverse this direction it will be necessary to change the use of the chambers which from compression sectors will become intake, the intake chambers will become compression sectors, the ducts and intake ports will become exhaust , while the ducts and the exhaust ports will become intake;

- ports 52,54 and 56,58 are equipped with non-return valves;

- ports 52,54 are respectively connected, with suitably sized hollow tubes, to ports 55,57;

- the internal stator 30 is rotated by 90 ° with respect to the previous configuration, this implies that the linear movement of the resilient elements 60, 61, has a direction perpendicular to the direction of the linear movement of the resilient elements 70, 71;

- the shades gray dotted white, gray dotted black, black indicate three increasing levels of pressure.

The fluid as shown in figure 11 is sucked into the external chambers (in black gray dotted white) to the elliptical section cylinder 10, flowing from the ports 51,53. In the chambers, external and internal to the rotary cylinder, the fluid is compressed to an intermediate pressure to the final one. In fact, from the first external chambers (gray dotted black) the fluid flows from the ports 52.54 to be conveyed to the ports 55.57 where it flows to the chambers (gray dotted black), inside the rotor 10. Subsequently the gas undergoes the last pressure gain in the internal chambers (in black) from which it will flow from the ports 56,58 to the final pressure, thus concluding its cycle.

In figure 11, in a first phase, the fluid from the ports 51,53 is sucked from the chambers external to the elliptical section cylinder (in gray dotted white). In the external chambers (in gray dotted black) the fluid that flows from the ports 52,54 is compressed and from there conveyed (by means of cable ducts) to the ports 55,57. From the lights 55,57 it flows into the internal chambers (in gray dotted black) to the rotary cylinder (10). In the chambers inside the rotor 10 (in black), the fluid is further compressed and flows from the ports 56,58 to be stored or used.

With reference to Figure 12, in a second step, fluid is sucked from the ports 51,53 into the outer chambers (in gray dotted white) to the rotary cylinder of elliptical section (10). From the 52.54 lights, the compressed fluid flows into the external chambers (in gray dotted black) which, by means of cable ducts, flows into the internal chambers (in gray dotted black) to the rotary cylinder from the 55.57 lights. The further compression of the fluid takes place in the internal chambers (in black) of the rotary cylinder from which it flows from the ports 56,58.

Referring to Figure 13, in a third step, the ports are all closed.

With reference to Figure 14, in a fourth step, the external chambers (in gray dotted white) to the rotary cylinder (10) suck the fluid from the ports 51,53. In the external chambers (in gray with black dots) the fluid is stressed and is thus subjected to the first pressure gain, it flows out of the ports 52,54. From the lights 55,57 the gas flows into the internal chambers (in gray dotted black) to the rotary cylinder (10). The ports 56,58 allow the outflow of the fluid from the internal chambers (in black) to the rotor.

Referring to figure 15, in a fifth phase, the first compression cycle ends, the rotary cylinder has performed a rotation of 180 °, in the subsequent rotation of 180 ° the phases will follow one another as in the descriptions from figure 11 to figure 14.

The advantages of this configuration are:

- gradual compression of the fluid in the subsequent passages, from the external to the internal chambers of the elliptical section rotary cylinder 10, to bring it to the desired pressure;

- greater efficiency in the dissipation of the heat produced by the compression of the fluid;

- absence of vibrations.

Configuration as motor, pneumatic or liquid-powered 1, hybrid

With reference to Figures 16 to 20, a further form of use of the device according to the invention is described below.

In this configuration:

- the external and internal chambers are fed by the ports 51,53,55,57, they discharge the fluid by means of the ports 52,54,56,58;

- the direction of rotation is clockwise, to reverse this direction it will be necessary to change the use of the chambers that from inflow sectors will become outflows, the inflow chambers will become outflows, while the ducts and inlet ports will become exhaust and the exhaust pipes and ports will become inflow;

- the compressor is powered by pressurized fluid; - the direction of movement of the resilient elements 60,61 is equivalent to that of the resilient elements 70,71.

In figure 16, in a first phase, the ports 55,56,57,58 are closed. From the ports 51,53, in the external chambers (in black) to the rotary cylinder 10, the pressurized fluid flows, thus generating a mechanical stress on the rotor which develops the driving torque. The fluid discharged from the ports 52,54 flows from the external chambers (gray dotted white) to the rotor 10.

Referring to figure 17, in a second phase, the ports 51,53,55,57 feed the relative chambers with the pressurized fluid through the pipes 51 ', 53', 55 ', 57' (in black). From the rooms in gray dotted white, through the ducts 52â € ™, 54â € ™, 56â € ™, 58â € ™ â € ™ connected to the lights 52,54,56,58, flows the fluid.

Referring to Figure 18, in a third step, the ports 51,52,53,54 are closed. Fluid under pressure flows from ports 55,57 into the chambers (in black) inside the rotary cylinder 10, from ports 56,58 the fluid present in the inner chambers (in gray dotted white) flows.

With reference to Figure 19, in a fourth phase, pressurized fluid flows from the ports 51,53,55,57 connected to the relative chambers (in black). The fluid flows from the lights 52,54,56,58, connected to the relative chambers (in gray dotted with white).

With reference to figure 20, in a fifth phase, after a rotation of 180 ° of the rotary cylinder 10, in the following 180 °, the descriptions listed from figure 16 to figure 20 will follow one another again.

The advantages of this configuration are:

- at each turning angle (360 °) of the drive shaft the volumetric capacity of the unit is double compared to the sum of the volumes of the external and internal chambers, which leads to a reduction in the external dimensions of the machine;

- homogeneous distribution of the torque transmitted by the rotor 10;

- absence of vibrations.

In relation to the previous application, it is necessary to further specify that the presence of several chambers (internal and external to the rotor), allows to realize other systems that contemplate the simultaneous use of fluids of different nature.

For example:

- exploit liquids under pressure or subjected to height jump, to compress gaseous fluids; - use pressurized fluids to pump liquids.

Air Motor Configuration 2

With reference to figures 21 to 25, a further form of application of the innovation according to the invention used as a pneumatic motor is described below.

In this configuration:

- the device is powered by pressurized fluid;

- the direction of rotation is clockwise, to reverse this direction it will be necessary to change the use of the chambers that from compression sectors will become suction, the suction chambers will become compression sectors, moreover the ducts and the suction ports will become exhaust while the ducts and the exhaust ports will become intake;

- the direction of movement of the resilient elements 60,61 is equivalent to that of the resilient elements 70,71;

- lights 56,58 are connected by means of cable ducts to lights 51,53.

The compressed fluid passes through the internal ports 55,57, expands in a first phase in the internal chambers (in black) of the rotary cylinder, flows from the ports 56,58, to be conveyed through the ports 51,53, into the chambers external to the rotary cylinder where it completes its expansion and then flows out of the ports 52,54.

With reference to Figure 21, in a first step, the ports 55,56,57,58 are closed. In the chambers (in gray dotted black) inside the rotary cylinder (10) the gaseous fluid has previously expanded to an intermediate pressure to the final one and will then flow out of the now closed ports 56.58. The fluid through the ports 51,53, connected to the previous 56,58, flows to the external chambers (in gray dotted black) developing a mechanical torque which stimulates the movement of the rotary cylinder 10. At the end of its expansion cycle, the gas flows out of the chambers external (in gray speckled white) through lights 52,54.

Referring to figure 22, in a second phase, from the ports 55,57, the compressed fluid flows into the internal chambers (in black) to the rotary cylinder 10, flows from the chambers (in gray dotted black) inside the rotary cylinder from the ports 56, 58, which connected to the lights 51,53, allow the gas to flow into the external chambers (in gray dotted black). The fluid present in the outer chambers (in gray dotted black) expands further. At the end of the second expansion phase, the gas present in the external chambers flows out of the ports 52,54 (in gray with white dotted lines).

With reference to Figure 23, in a third step, the ports 51,52,53,54 are closed. From the ports 55,57 in the internal chambers flows compressed fluid (in black) which solicits the movement of the rotary cylinder (10). From ports 56.58, the gas that has undergone the first phase of expansion flows and conveyed to ports 51.53.

With reference to Figure 24, in a fourth step, the compressed fluid flows from the ports 55,57 and expands into the chambers (in black) inside the rotary cylinder (10). From the ports 56,58, the fluid present in the chambers (gray dotted black) inside the rotor (10) flows out. From the ports 51.53, the gas flows, conveyed by the ports 56.58, which will undergo the last phase of expansion in the external chambers (gray dotted black) to the rotary cylinder. Fluid flows from the ports 52,54 at the end of the expansion cycle.

With reference to figure 25, in a fifth phase, after a rotation of 180 ° of the rotary cylinder 10), in the subsequent rotation of 180 °, the phases are repeated starting from figure 21 up to figure 24.

The advantages of this configuration are:

- the compressed fluid expanding in successive phases produces a homogeneous mechanical traction torque. In fact, in the first stage of expansion, in the internal chambers, the fluid has a higher pressure than in the external ones. Therefore the mechanical torque produced uses a smaller arm. In the second stage the gas pressure is lower, but by acting on the external surface of the rotary cylinder it produces a torque with an arm greater than the first;

- the subsequent expansion phases of the fluid allow the heat lost by compression during storage to be gradually recovered; - absence of vibrations.

Configuration of an exothermic closed cycle motor 1 Referring to figure 26, the configuration of the device according to the invention in this case provides that the external and internal chambers are in phase.

In this configuration:

- the vanes 70, 71 of the internal stator 30, inside the elliptical rotor 10, are out of phase by 90 ° with respect to those 60, 61 of the cylinder 20 external to the rotor;

- the direction of rotation of the rotor is clockwise;

- ports 51,53,56,58 are connected to a hot exchanger Scâ € ™, ports 52,54,55,57 to the cold exchanger Sc by means of hollow pipes.

In this way a watertight system is obtained in which there is a compressed gaseous fluid.

We consider the plant described at an initial quiet phase in which the pressure p is equivalent on the whole plant. We then expose the heat exchangers, Scâ € ™ hot and Sc cold, to the relative thermal sources (tâ € ™, t, with tâ € ™> t), thus creating an increase in pressure pâ € ™> p in the system connected to the hot exchanger. In this way the pressures pâ € ™ and p acting on the external and internal surfaces of the rotor 10 develop the driving torques which allow its rotation.

In fact, it should be noted that in the external chambers (in gray), supplied by lights 51,53, there is the same pressure pâ € ™ as the chambers (in black), inside the rotor 10, communicating with the lights 56, 58. In the external chambers (gray with white dotted), supplied by lights 52.54, there is the same pressure p as the internal chambers (gray with white dotted) at rotor 10 communicating with lights 55.57.

The sum of the pairs of forces, with a sign relative to the direction of rotation impressed on the rotor, generated by the pressures present in the external chambers and acting on the external surface of the rotary cylinder 10, develop a pair of forces greater than the sum of the pairs of forces generated by the pressures present in the internal chambers, acting on the internal surface of the cylinder. This occurs because:

the arm of the resultant of the external forces, with fulcrum on the axis of rotation of the rotor 10, is greater than the arm of the resultant of the forces acting on the internal surface of the cylinder 10;

the external surfaces on which the pressures act are of greater extension than the internal ones.

In this way the pressures in the external chambers (greater volume) generate the motive action of the rotor, which allows the hot (expanded) fluid to flow from the exchanger Scâ € ™ (hot) to the exchanger Sc (cold). In fact, the chambers inside the rotor (with a lower volume) acting as a compressor / pump for the cold fluid (contracted), allow the flow of the cooled fluid from the heat exchanger Sc (cold) to the heat exchanger Scâ € ™ (hot). With the engine running, the quantity of gas molecules flowing from the external chambers, through the ports 51,52,53,54, and from the internal chambers, through the ports 55,56,57,58, is equivalent.

Considering as reference the rotor 10 of figure 26 and assigning the value of 0 ° to its angular position, in the present application, when it rotates clockwise by 90 ° and in the following 270 ° the torque value generated by the jump of pressure pâ € ™> p. In fact, in these two (critical) positions 90 ° and 270 °, the fluid cannot flow in or out of the internal and external chambers, since the rotor 10 closes the respective supply ducts. Therefore, to avoid the stopping or non-starting of the rotor 10 in the critical points even with the application of the external load, the unit can be equipped with a massive flywheel or other technical device useful for maintaining the angular momentum or providing the an idea to overcome these criticisms. This problem can otherwise be solved by making two units work at the same time, with their respective rotors out of phase by 90 ° and integral, so that they reciprocally provide the mechanical torque necessary to overcome the respective critical positions.

The advantages of this configuration are:

- cyclical yields higher than other closed-cycle exothermic thermodynamic machines;

- reduction of overall dimensions;

- acoustic comfort;

- absence of vibrations.

Configuration of closed-cycle exothermic engine 2 Referring to figures 29 to 34, configuration 100â € ™ of the device according to the invention in this case provides for the coupling of two devices of the type described above, one operating as a compressor ( sector 110 ') and the other (sector 120') as an engine.

The rotors 10â € ™ a and 10â € ™ b with elliptical crown geometry, of this configuration, are respectively displaced in position by an angle of 90 °. They are also integral with each other by means of the same crankshaft 130â € ™ (see figure 34), in which the part that compresses the gas (cold part 110â € ™) is dragged by that (hot part 120â € ™) which develops the engine torque.

Separated by a 140â € ™ partition or by technical devices that act as thermal insulation, the hot and cold sectors of the unit and the system with the heat exchangers connected to it are exposed to the relative sources to obtain mechanical work.

In this configuration:

- the sum of the volumes of the external and internal chambers of the hot sector is greater than the sum of the volumes of the relative chambers present in the cold sector: their correct sizing is necessary for the operation of the machine; - the resilient contrast elements 70â € ™, 71â € ™ of the stator 30â € ™ a, inside the elliptical crown rotor 10â € ™ a, are in line with the resilient elements 60â € ™, 61â € ™ of the stator 20â € ™ a external to the rotor;

- the resilient contrast elements 90â € ™, 91â € ™ of the stator 30â € ™ b, inside the elliptical rotor 10â € ™ b, are in line with the resilient elements 80â € ™, 81â € ™ of the cylinder 20â € ™ b external to the rotor;

- the direction of rotation of the crankshaft, in this configuration, is anticlockwise if we consider as a reference an observer placed on the side of the cold sector 110â € ™;

- lights 32 ', 34', 36 ', 38', in the sector that develops the drive pair (hot sector 120 ') and lights 51', 53 ', 55', 57 ' ™, in the sector that compresses the fluid (cold sector 110â € ™), are connected to the Scâ € ™ (hot) exchanger, through suitably sized cable ducts;

- lights 31 ', 33', 35 ', 37', in the hot sector (120 ') and 52', 54 ', 56', 58 ', in the cold sector (110') are connected to the exchanger Sc (cold), by means of hollow ducts through which the carrier fluid flows;

- the Scâ € ™ (hot) exchanger is powered by the hot thermal source;

- the exchanger Sc (cold) is cooled by the cold heat source.

In this way a watertight system is obtained in which there is a compressed gaseous fluid.

Let us consider the machine and the plant described at an initial stage of quiet. Therefore subjected to the temperature t of the cold source, the pressure p develops over the whole sealed system.

In the next phase we expose the hot sector of the unit, the system that connects it to the Scâ € ™ (hot) exchanger, at the temperature tâ € ™ of the hot source. The cold sector and the exchanger Sc (cold) will be cooled to the temperature t from the cold source.

In the part of the system connected to the Scâ € ™ (hot) the pressure pâ € ™ of the fluid increases (pâ € ™> p) due to the heat supplied by the relative source. The pressure jump p '> p thus generated will produce as an effect the mechanical stress of the rotors 10'a and 10'b. Due to the different sizing of sectors 110 'and 120' and of the relative rotors, a non-zero drive torque will be obtained. The force being equivalent to the product of the pressure p and p 'for the surface on which they act, and the driving torque obtained from the sum of the driving torques, based on the direction of rotation impressed on the rotary cylinders 10'a and 10â € ™ b. The single driving torques result from the product of the forces and the distances between the rotation axis of the rotors 10'a and 10'b, and the points on which the pressures p and p 'act.

In the example described, the sum of the moments will give the counterclockwise direction of rotation, observed from the cold sector.

The fluid present in the hot exchanger Scâ € ™ will flow at pressure p 'into the cold exchanger Sc at pressure p, passing through the chambers of the hot sector of the unit (120') and stressing the motion of the rotor 10'b. The rotation of the rotor 10'b, by means of the shaft 130 ', generates the rotation of the rotor 10'a. The fluid present in the cold exchanger Sc at pressure p will be compressed to the pressure p 'in the hot exchanger Sc', passing through the chambers of the cold sector of the unit (110 ') and stressed by the rotor 10'a.

Thanks to the constructional peculiarities of the machine and the presence of hot and cold thermal sources, the fluid present in the system creates a cyclic path. Starting from the hot exchanger Scâ € ™, a certain quantity of expanded gas molecules (pressure pâ € ™) crosses the chambers (with greater volume) of the hot sector (120 ') of unit 100â € ™. The same quantity of molecules contracts, in the cold exchanger Sc, at pressure p, due to the cooling exerted by the relative thermal source. The gas molecules thus cooled are then compressed again at the pressure pâ € ™ in the chambers (with lower volume) of the cold sector (110 '), and conveyed into the hot exchanger Scâ € ™. The same quantity of gas molecules poured into the hot exchanger Sc ', due to the heat of the relative thermal source, will expand again, ending the cycle.

In summary, during the rotational motion of the rotors 10â € ™ a and 10â € ™ b inside the chambers of the respective sectors 110â € ™ and 120â € ™, the quantity of gas molecules that flows from Scâ € ™ into the sector 120â € ™ with a higher flow rate and flows in cold Sc, it is equivalent to the quantity of gas molecules that is made to flow in cold Scâ € ™ and flow out from hot Sc, through the chambers of the cold sector 110â € ™ with a lower flow rate. Therefore the pressures, pâ € ™ in the hot exchanger Scâ € ™ and p in the cold exchanger Sc, remain unchanged in the presence of the relative thermal sources.

Referring to figure 29, you can see the two external sides of the unit from where the lights are visible, and in transparency the supply or discharge ducts of the chambers present in sectors 110â € ™ and 120â € ™. It is possible to observe the two sectors with the relative rotors 10â € ™ a and 10â € ™ b arranged respectively at 0 ° and 90 °.

Therefore in the hot sector 120â € ™ the ducts serving lights 35â € ™, 36â € ™, 37â € ™, 38â € ™, are closed. From the 32â € ™, 34â € ™ lights in the black chambers the fluid flows at pressure pâ € ™ by means of cable conduits connected to the hot Scâ € ™. From the chambers in gray dotted white of sector 120â € ™ the fluid flows at pressure p which from the ports 31â € ™, 33â € ™, by means of connecting cable ducts, is conveyed to the cold SC. In the cold sector 110â € ™ the passages serving lights 55â € ™, 56â € ™, 57â € ™, 58â € ™ are closed. In the black chambers the fluid is compressed to pressure pâ € ™ and by means of the ports 51â € ™, 53â € ™ and through cable ducts it is conveyed into the hot Scâ € ™. From the gray dotted white chambers the fluid is sucked at the pressure p present in cold Sc, passing through cable ducts and through the ports 52â € ™, 54â € ™.

Referring to figure 30, it is possible to observe the two sectors 110 'and 120' with the relative rotors 10â € ™ a at -45 ° and 10â € ™ b also apparently arranged at -45 ° because in b it is reproduced in front view. Seen from the front from the position of the rotor 130 'and in transparency, it would be at 45 °.

Then in sector 120â € ™ from ports 32â € ™, 34â € ™, 36â € ™, 38â € ™, by means of the hollow tubes connected to the hot Scâ € ™, the fluid flows into the black chambers at pressure pâ € ™. From the gray dotted white chambers of the hot sector 120â € ™, the fluid flows at pressure p and from the ports 31â € ™, 33â € ™, 35â € ™, 37â € ™, by means of the hollow connection pipes, it is conveyed to the cold SC . In the cold sector 110â € ™ from the chambers in gray dotted white the fluid is sucked at the pressure p present in cold Sc, passing through cable connections and through the ports 52â € ™, 54â € ™, 56â € ™, 58â € ™. In the black chambers the fluid is compressed at pressure pâ € ™ and by means of the ports 51â € ™, 53â € ™, 55â € ™, 57â € ™ and the cable connections it is conveyed into the hot Scâ € ™.

Referring to figure 31, it is possible to observe the two sectors with the relative rotors 10â € ™ a at 90 ° and 10â € ™ b at 0 °.

So in the hot sector 120â € ™ the ducts serving lights 31â € ™, 32â € ™, 33â € ™, 34â € ™ are closed. The fluid at pressure pâ € ™ flows from the 36â € ™, 38â € ™ lights in the black chambers by means of cable ducts connected to the hot Scâ € ™. In the cold sector 110â € ™ the ducts serving lights 51â € ™, 52â € ™, 53â € ™, 54â € ™ are closed. In the black chambers the fluid is compressed at pressure pâ € ™ and by means of the ports 55â € ™, 57â € ™ and the cable connections it is conveyed into the hot Scâ € ™. From the chambers in gray dotted white the fluid is sucked at the pressure p present in cold Sc, passing through the cable ducts and through the ports 56â € ™, 58â € ™.

Referring to figure 32, it is possible to observe the two sectors 110 'and 120' with the relative rotors 10â € ™ a at -135 ° and 10â € ™ b apparently arranged at 45 ° but in reality, seen from the front position of the shaft engine 130 'and in transparency, it would be at -45 °. In the hot sector 120â € ™, from the ports 32â € ™, 34â € ™, 36â € ™, 38â € ™, by means of the cable ducts connected to the hot Scâ € ™, the fluid flows into the black chambers at pressure pâ € ™. From the gray dotted white chambers of sector 120â € ™ the fluid flows at pressure p which, from the ports 31â € ™, 33â € ™, 35â € ™, 37â € ™, is conveyed to the cold SC through the connecting cable ducts. In the cold sector 110â € ™ from the chambers in gray dotted white the fluid is sucked at the pressure p present in cold Sc, passing through the cable ducts and through the ports 52â € ™, 54â € ™, 56â € ™, 58â € ™. In the black chambers the fluid is compressed at pressure pâ € ™ and by means of the ports 51â € ™, 53â € ™, 55â € ™, 57â € ™ and the cable ducts it is conveyed into the hot Scâ € ™.

The advantages of this configuration are:

- cyclical yields higher than other exothermic thermodynamic cycles;

- reduction of overall dimensions;

- acoustic comfort; absence of vibrations.

The differences with respect to the solution â € œConfiguration of an exothermic closed cycle motor 1â € are found in the choice of the physical characteristics of the material with which the rotary cylinders 10â € ™ a and 10â € ™ b are made, with respect to the rotor 10.

In the first solution (exothermic motor 1) it is necessary to make the rotary cylinder 10 with a material that has characteristics of resistance to mechanical stress and a very low thermal conductivity, to minimize the thermal bridge between the external and internal chambers of the rotor 10. In this solution (exothermic motor 2) the thermal bridge between sectors 110 'and 120' is reduced by component 140â € ™.

Finally, it is observed that as in the previous description, the thermodynamic cycle of this second unit is reversible. In fact, by applying an external mechanical torque to the motor shaft, it is possible to generate a thermal jump in the heat exchangers of the system. In this way a cryogenic machine is created.

The present invention can be used for multiple applications:

- a reversible pneumophora machine;

- a reversible pump for incompressible fluids; - as a reversible compressor / pump for fluids, allowing the simultaneous use of two fluids of different nature;

- an exothermic closed-cycle engine, which allows the exploitation of two thermal sources with low ∠† t (temperature difference) to produce mechanical work;

- a refrigerating machine operated by an external mechanical couple to produce a thermal jump. In the foregoing, the preferred embodiments have been described and variants of the present invention have been suggested, but it is to be understood that those skilled in the art will be able to make modifications and changes without thereby departing from the relative scope of protection, as defined by claims attached.

Claims (1)

CLAIMS 1) Rotary device for compression or pumping (100) of a fluid, characterized in that it comprises; an external stator (20) with a cavity at the center of which it is axially positioned an internal stator (30), between the outer stator (20) and the inner stator (30) being arranged coaxially in a rotatable manner; a rotor with crown section (10), which is kept rotating by a external motor, and in which: the shape of the external surface of the internal stator (30) corresponds to that of the internal surface of the external stator (20), the shape of the rotor with crown section (10) having an ellipticity different from that of the internal stator (30) and of the external stator (20), in such a way that said rotor with crown section (I) contacts both the internal wall of said cavity of the external stator (20) in two diametrically opposite external points and the external surface of said internal stator (30 ) respectively in two diametrically opposite internal points, the external stator comprises in diametrically opposite positions a first and a second resilient element (60,61) arranged on the same plane or otherwise curvilinear and extended in the direction of the axis of the internal stator [30) and which continuously contact the external surface of said rotor with crown section (10), said first and second resilient element (60,61) being respectively movable in two opposite directions or opposite rotations between a first position flush with the inner wall of said cavity and a second elongation position at the inside of said cavity, on one side and on the other side of said first and second resilient element 2 or 4 corresponding chambers being each time formed; the internal stator (30) comprises in diametrically opposite positions a first and a second further resilient element (70,71) arranged on the same further plane or otherwise curvilinear and extended in the direction of the axis of the internal stator (30) and which continuously contact the internal surface of said crown rotor (10) in two or more respective lines, said first and second further resilient element (70,71) being respectively movable in two opposite directions or opposite rotations between a first position flush with the external surface of said internal stator (30) and a second elongation position beyond said external surface of said internal stator (30), on one side and on the other of said first and second further resilient element, further corresponding chambers being formed each time, mpressor further understanding: in correspondence with the first resilient element (60), on one side of said plane, a first external port (51) for the passage of the fluid connected to said cavity through a relative series of first external port ducts (51 ''), on the side opposite of said plane, a second external port (54) for the passage of the fluid connected to said cavity through a relative series of second external port ducts (54 ''); as well as, in correspondence with said second resilient element (61), on said opposite side of said plane, a third external port (53) for the passage of the fluid connected to said cavity through a relative series of ducts of third external port (53 ' '), on said side of said plane, a fourth external port (52) for the passage of the fluid contained in said corresponding chambers, connected to said cavity through a relative series of fourth external port ducts (52' '); in correspondence with the first further resilient element (70), on one side of said further plane, a first internal port (55) for the passage of the fluid connected to said cavity through a relative series of first internal port ducts (55 ''), on the opposite side of said further plane, a second internal port (58) for the passage of the fluid connected to said cavity through a relative series of second internal port ducts (58 ''), and in correspondence with said second further resilient element (71 ), on said opposite side of said further plane, a third internal port (57) for the passage of the fluid connected to said cavity through a relative series of third internal port ducts (57 ''), on the side of said further plane, a fourth internal port (56) for the passage of the fluid contained in said corresponding chambers, connected to said cavity through a relative series of fourth internal port (56 ''), the fluid being drawn from time to time through two internal ports and two external ports and being evacuated through the remaining two internal ports and two external ports as a result of the thrusts exerted on the fluid between said crown rotor and said internal and external stator and said resilient elements, the ports being such that: - said first external port (51), said second external port (53), said third external port (52) and said fourth external port (54) are arranged close to the respective resilient elements and in a direction substantially perpendicular to the direction of the axis of rotation of the device, - said first internal opening (55), said second internal opening (57), said third internal opening (56) and said fourth internal opening (58) are arranged close to the respective resilient elements and in a direction substantially perpendicular to the direction of the rotation axis of the device. 2} Device according to claim 1, characterized in that said internal (30) and external (20) stator have cylindrical facing surfaces, and said crown rotor (10) has an elliptical crown. 3) Device according to claim 2, characterized in that said plane coincides with said further plane. 4) Device according to claim 3, characterized by the fact that the rotor is able to turn clockwise, observed in front of the lights, and by the fact that said second external light (54), fourth external light (52), second internal port (58) and fourth internal port (56) are equipped with non-return valves, so that the compressed fluid does not reverse the flow direction, and by the fact that, the fourth external port (52) and the second external port ( 54) are connected by means of suitably sized cable ducts to the first internal light (55) and to the third internal light (57), while, with the counterclockwise rotation of the rotor (10), observing it in front of the lights, it is characterized by the fact that: said first external light (51), third external light (53), first internal light (55) and third internal port (57) are equipped with non-return valves, so that the compressed fluid does not reverse the flow direction, and by the fact that the first external port (51) and the third external port (53) are connected by means of of suitably sized cable ducts to the second internal opening (58) and to the fourth internal opening (56). 5) Device according to claim 2, characterized in that said plane is transversal to said further plane. 6) Device according to claim 5, characterized in that, with the clockwise direction of rotation of the rotor (10): - said second external port (54), fourth external port (52), second internal port (58) and fourth internal port (56) are provided with non-return valves, so that the compressed fluid does not reverse the direction of flow; - said fourth external port (52) and said second external port (54) are respectively connected, with suitably sized hollow ducts, to said first internal port (55) and to said third internal port (57); with the anticlockwise direction of rotation of the rotor (10); - said first external port (51), third external port (53), first internal port (55) and third internal port (57) are provided with non-return valves, so that the compressed fluid does not reverse the direction of flow; - said first external port (51) and said third external port (53) are respectively connected, with suitably sized cable ducts, to said second internal port (58) and to said fourth internal port (56). 7) Use of the rotary device (100), defined by claim 3, as a motor, characterized by the fact that said fluid is a fluid under pressure through four ports (51,53,55,57), the fluid under pressure generating a torque driving on the crown rotor (10) and being discharged as a consequence of its motion, through the remaining four ports (52,54,56,58). 8) Motor device, comprising the rotary device (100) as defined by claim 3, characterized by the fact that said fluid is a fluid under pressure, and by the fact that, when the direction of rotation of the rotor is clockwise observed from the exposed lights: - the first internal port (55) and the third internal port (57) are adapted to receive the fluid under pressure; - the fourth internal port (56) and the second internal port (58) are suitable for evacuating the pressurized fluid; the fourth internal port (56) and the second internal port (58) are connected through suitable pipes to the first external port (51) and third external port (53); - the fourth external port (52) and the second external port (54) are suitable for evacuating the fluid in compression coming from the first external port (51) and the third external port (53). 9) Motor device adapted to be used in an exothermic closed cycle, comprising the rotary device (100) as defined by claim 5 in which a gaseous fluid circulates, connected by hollow ducts to a hot heat exchanger and a cold heat exchanger, characterized by the fact that: said internal (30) and external (20) stator have cylindrical facing surfaces, and said crown rotor (10) has an elliptical crown; four ports (51,53,56,58) are connected to the hot exchanger (Sc '), the remaining four ports (52,54,55,57) are connected to the cold exchanger Sc, by means of cable ducts; the gaseous fluid flows from the hot exchanger (Sc ') at pressure pâ € ™ at the cold one (Se), passing through the chambers external to the rotor (10) thus causing its movement, the motion of the crown rotor (10) causing the flow of fluid from the cold (Sc) to the hot (Sc ') exchanger, which passes through its internal chambers. 10) Use of the motor device (100) according to claim 9 as a cryogenic machine, characterized by the fact of applying a driving torque to the crown rotor (10) to create a temperature difference between the heat exchangers. 11) Motor device (100 ') adapted to be used in a closed exothermic cycle, characterized in that it comprises a first sector (110') and a second rotary sector (120 '}, with respective elliptical ring rotors (10'a , 10'b) each as defined by claim 3, and in which a gaseous carrier fluid circulates, the first sector (110 ') being connected by hollow ducts to a cold heat exchanger (Sc) and the second device (120' ) connected by hollow ducts to a hot heat exchanger {Sc '), said first (110') and second [120 ') sectors being integrally arranged coaxially with an intermediate separation element (140'), so that the rotors (10'a) and {10'b) are free to rotate integrally with the shaft (130 '), the planes of the respective resilient elements and the relative rotors (10'a) and [10â € ™ b) of the first sector (110 ') and the second sector (120') being respectively displaced in position by an angle of 90 °, and by the fact that: the sum of the volumes of said corresponding chambers of the second sector [120 ') is greater than the sum of the volumes of the relative chambers of the first sector (110'J, their correct dimensioning is a necessary condition for the correct functioning of the machine at steady state; four lights (51 â € ™, 53 ', 55 â € ™, 57') of the first device U 10 ') are connected by cable ducts to the hot exchanger (Sc'), the remaining four lights (52 ', 54', 56 ', 58') of the first device [110 ') are connected to the cold exchanger (Sc), by means of suitably sized cable ducts; four lights (32 ', 34', 36 ', 38') of the second device [120 ') are connected to the hot exchanger (Sc'), the remaining four lights (3 ', 33', 3 ', 37'} are connected to the cold exchanger (Sc), by means of suitably sized cable ducts; the hot exchanger {Sc ') is powered by a hot thermal source; â € ”the cold exchanger (Sc) is cooled by the cold thermal source; â € "The gaseous fluid flows from the hot exchanger (Scâ € ™) to the cold one (Sc) passing through the device chambers (120 ') and flows into the cold exchanger (Sc) from the hot exchanger (Sc') passing through the chambers of the device (110 "), generating the rotational movement of the shaft (130 '). 12) Use of the motor device (100 ') according to claim 11 as a cryogenic machine, characterized by the fact of applying a driving torque to said shaft (130') to generate a temperature difference between the heat exchangers (Sc, Sc ') .