ES2626961B1 - Inertial piston compressor and rotary cylinders - Google Patents

Abstract

Inertial piston and rotary cylinder compressor that compresses the gas in the compression chamber, while aspirating the gas into the intake chamber. The gas is compressed by a compression piston subjected to centrifugal acceleration. The force that displaces said piston is due to its inert mass added to that of several inertia pistons, attached to the compression piston, multiplied by centrifugal acceleration. The pistons perform a sequential alternative movement by combining, within the centrifugal field, a circular displacement over the center of rotation of the field, with a rotation on its own common axis of transverse inertia. This axis is supported by rotating platforms that produce the centrifugal field. The aforementioned axis, rotates on itself by having Faraday discs subjected to an electromagnetic field in circular sectors of said discs. The discs are engaged in a central freewheel sprocket that gives a mechanical balance to the rotating assembly.

Description

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DESCRIPTION

Inertial piston compressor and rotary cylinders.

Technical sector

The compression of any type of gas.

State of the art

The state of the art related to the invention is published in the WIPO Gazette, dated 06/25/2015, with the number WO2015092088 of the patent PCT / ES2014 / 00211, entitled "Celestial Motor-Compressor of circular impulse" and in the SPTO of the SPTO dated 10/02/2016 with the patent number P201400560 and title "Gas compressor by inertial piston".

Related to the invention is the technique of gas compressors, of the different types that exist on the market, among which we mention informative and non-limiting nature of alternative piston compressors using crankshaft and connecting rod, axial type centrifuges or radial, screw, membrane, lobes, vanes and liquid piston.

Explanation of the invention.

The explanation of the invention, as it is characterized in the claims, is carried out by exposing the technical problems raised and the solutions applied which, being interrelated in the gas compressor described by the cited patents, integrate a single general inventive concept. The explanation is completed, indicating the advantages of the invention in relation to the prior art.

Technical issues raised:

1. The use of gases at high and very high pressure and for certain industrial applications, requires the total elimination of fatty components in compressed gases. It is necessary, therefore, that the compressor minimize the probability of gas contamination during the compression process. In the inertial piston gas compressor of the published patent P201400560 and in the contents of the PCT / ES2014 / 00211, the polluting sources of the gas may be external and / or internal to the compressor itself. The internal sources are mainly located in the lubricants for the linear bearings installed inside the cylinders. Therefore, there is a need to eliminate any mechanism that requires lubricant to operate inside the cylinders that compress the gas.

2. The use of gases at high and very high pressure and for certain industrial applications requires regulating the output flow of the compressor to adjust it to the production needs and without the said regulation affecting the compressed gas outlet pressure. The transmission by gears and circular rack for the rotation of the cylinders, which appear in the patents cited and published in the State of the Art, does not allow the regulation of the volumetric displacement of the compressor to be independent of the outlet pressure and its lubrication system It can contaminate the gas in aspiration. Therefore, there is a need to implement a system that allows the aforementioned regulation, while reducing the probability of gas contamination in the suction valves.

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Solutions to the problems raised:

1. To eliminate the possible contamination of the gas, which can come from the lubricant of the linear bearing that supports the piston inside the cylinder, the said linear bearing inside the cylinder (13) is eliminated. The compression piston (14) adjusts its linear displacement on the inner sleeves of the cylinder (13). The tight seal of this adjustment can be achieved by dry teflon gaskets with carbon and graphite fillers or bronze or appropriate material loads to ensure smooth sliding. Alternatively, this seal can be reinforced for highly volatile gases, using elastic or bellows membranes for closing the intake chambers (15) and compression chambers (16) and whose expansion and contraction movements are linked to the movements of the compression pistons (14). The sealing joints of dry type, work with reduced friction losses for the forces in the direction of the longitudinal axis of the cylinder which is the direction of the movement of the piston but do not support the high transverse forces on said piston and in the event that they can bear them, cause high friction losses. To withstand the high transverse forces, while simultaneously ensuring smooth sliding of the compression piston (14) and with reduced friction losses, several open linear bearings (30) are installed outside the cylinder (13). These open linear bearings (30) are fixed on the supports of the inertia and cylinder pistons (29) that are rigidly connected to the secondary shafts (11). Several linear bearings can be installed on a single support of cylindrical piston and cylinder (29), distributed on the vertices of a regular polygon that forms said support that is centered on the secondary axis (11). Each open linear bearing (30) glues to a piston of inertia (33). The centrifugal force of the rotation of the rotating platforms, combined with the rotation of the supports of the inertia and cylinder pistons (29), alternately and sequentially move the compression piston (14) and each of the inertia pistons ( 33) on its linear bearing. This movement is limited by buffers of shock absorbers (34) for the inertia pistons (33) and by the compressed gas and the bottom of the cylinder head (36) for the compression piston. Each inertia piston (33) is rigidly attached to the compression piston (14), by means of a mechanical stump (38). This stump (38) transmits the force of the inertia of the mass of the inertia piston (33), in the direction of the longitudinal axis of the cylinder (13), to the compression piston (14). For this the cylinder (13) has as many grooves of the cylinder (37) as inertia pistons are installed. These cylinder grooves (37) are centered therein, in the sense of their length and are of the appropriate size to allow each stump (38) to travel the distance equivalent to a compression stroke. The compression piston (14), moved by the thrust resulting from the sum of its own force and the sum of all the forces of all the inertia pistons, compresses the gas in the compression chamber (16) while it is produced the gas inlet to the cylinder in the intake chamber (15). The compression chamber (16) discharges the compressed gas through the discharge valve (18), high pressure duct (26), secondary rotary joint (19) and high pressure duct (20) inside the central axis ( 27). Compressed gas passes through the primary rotary joint (25) and high pressure distributor (12) to the high pressure tank (7) that has outlet couplings (5) for the supply of compressed gas.

2. To regulate the volumetric displacement of the compressor, making it independent of the supply pressure and at the same time reducing the probability of contaminating the gas in the suction valves, the gears and circular rack contained in the published patents PCT / ES2014 / 00211 and / or P201400560, for flat and small thickness discs (10), installed at the lower ends of the secondary shafts (11). Each of said discs is preferably formed by a steel core on which two aluminum plates are fixed. Electric coils or alternatively permanent magnets generate magnetic poles (9) that

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produce an axial magnetic flux (N) - (S). This magnetic flux crosses a circular sector of each of the disks (10). The circular translation displacement of the disks (10), induces forces contrary to this displacement, in the circular sector of each of the disks (10) that is located within the axial magnetic flux. A couple of forces are generated that produce the rotation of the discs. These pairs of forces are produced by the rotational forces of the lower rotating platform (31) and the upper rotating platform (32) when moving in a circular line to the secondary axes (11) and by the forces, in the opposite direction to the previous ones that are applied in the circular perimeters of the disks (10) and are generated by the interaction of the magnetic flux ((N) - (S)), with the free electrical charges in the mentioned disks.

For a given dimension, manufacture and nature of the material of the disks (10), the value of the torque and the revolutions of the disks (10) and cylinders (13), coupled on the secondary shafts (11) are directly proportional at the relative speed of the free electrical charges of the conductive material of the disks in relation to the axial magnetic flux and the square of the electromagnetic induction of said magnetic field (N) - (S). The speed of rotation of the cylinders (13) is regulated and with it the volumetric displacement of the compressor, modifying the value of the magnetic induction that passes through the disks (10) and / or modifying the relative speed of displacement of the disks (10) in relation to the aforementioned magnetic field. The use of permanent magnets allows to regulate the speed of rotation of the cylinders, modifying the reluctance value of the magnetic circuit and / or modifying the revolutions of the electric motor (1). The reluctance of the magnetic circuit can be modified by introducing slight variations in the thickness of the air gap and the revolutions of the electric motor (1) can be modified by varying the frequency of the alternating current of supply to said motor. Alternatively using induction coils, the intensity of the magnetic field can be modified with the aforementioned and also varying the amp-turns on the coils when direct current is used or alternatively modifying the current intensity and / or the frequency and / or the direction of rotation of the phases, when alternating current is used in the coils.

The replacement of the cogwheels and the circular rack that are in the current state of the art, by the electromagnetic coupling explained, can introduce a dynamic imbalance by causing instantaneous displacements of the center of gravity of the rotating masses of the geometric center of rotation (the central axis). This instantaneous imbalance can occur if the resistant moment of the cylinders for the rotation on its transverse axis is not coincident in time for all the disks, which results in a different instantaneous rotation speed for each cylinder. The electromagnetic coupling tends to correct this imbalance by increasing and / or decreasing the electric slip on the disc that decreases and / or increases its rotation speed. But there is a delay time in the electromagnetic response during which the rotating system is not in mechanical equilibrium. In order to achieve this balance at all times and independent of the motor pairs versus resistant pairs on the discs, each of said discs (10) is a gearwheel that is engaged with a central toothed pinion (28), which can freely rotate in the center of the magnetic poles (9). This toothed pinion (28) creates a mechanical bond between the discs, instantly compensating for possible variations in the speed of rotation of one of the discs relative to the whole. The difference between this solution and that existing in the current state of the art, in addition to the aforementioned electromagnetic coupling, is that the circular rack rigidly attached to the support structure of the current state of the art, is replaced by a freewheel and cogwheel small module

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3. Secondary rotary seals (19) and primary rotary seals (25) are dry seals using Teflon or similar alternative material, with various adjustment rings that do not require lubricants for a tight seal and smooth sliding. The axial-radial type bearings of the central and secondary shafts are of closed manufacture and with lubricant at source for the entire life of the aforementioned bearings.

4. The gas to be compressed passes through the primary filters (6) into the enclosure of the compressor. The axial flow propellers (35) produce an upward movement of the gas to be compressed and an overpressure at the inlet of the intake valve (17). Alternatively, on these intake valves (17) secondary filters can be installed, which will make a second filter of the gas to be compressed. The upstream of the gas to be compressed facilitates the cooling, by the gas itself, of the compression chambers. The heat, by means of this gas stream, is expelled by the ventilation holes (8) made in the upper part of the protection cover (4) and which, alternatively, can be provided with overpressure gates.

Advantages of the invention in relation to the prior art state:

The electromagnetic coupling to produce the rotation of the cylinders significantly reduces the probability of contaminating the gas to be compressed from fatty particles, reduces mechanical losses and improves the efficiency of the compressor. Simultaneously, it provides a solution that allows the volumetric displacement of the gas to be controlled independently of the outlet pressure of said gas.

The installation of the linear bearings on the outside of the cylinder eliminates the possibility of contaminating the gas, with the lubrication grease of the mentioned bearings. The lateral walls of the compression piston must not withstand the high transverse forces caused by the centrifugal force at the beginning of the compression stroke. The result of the compression forces of several inertia pistons is applied to the compression piston, which makes it possible to obtain a pressure in the compression chamber for a given surface of the said piston than with the use of a single piston. compression. In theory, the counter-pressure of the gas, in the compression chamber, tends to balance the resulting inertial force (quasi-static compression of infinite stages for each stroke), which means high efficiency in the compression process. In practice, the latter force is greater, which causes the compression piston to reach a certain speed at the end of its travel. The kinetic energy associated with this speed is recovered at the shock springs at the end of the stroke of the inertia pistons and is returned to the compression process in the next cycle, which improves their energy efficiency and provides a significant competitive advantage.

The installation of inlet filters of the gas to be compressed to the interior of the compressor, alternatively associated with secondary filters in the same suction valve, reduces the presence of environmental pollutant particles in said gas. The axial flow upward propellers allow compensation of the pressure losses of the filters, improve the work of the suction valve and cool by forced convection to the compression chambers.

Brief description of the drawings

For better clarification of the previous explanation, a set of drawings is incorporated into the description where, for illustrative and non-limiting purposes, they represent the following:

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Figure 1. External elevation view of the compressor with the electric motor (1), engine support (2), central shaft (3), protective cover (4), compressed gas inlets (5), primary filters (6) and high pressure tank (7).

Figure 2. Exterior plan view of the compressor, with the plot of the cutting plane generated by Figure 3 and the ventilation openings (8).

Figure 3. Elevation according to section AA of Figure 2 with the magnetic poles (9), discs (10), secondary shafts (11), high pressure distributor (12), cylinder (13), compression piston (14), intake chamber (15), compression chamber (16), intake valve (17), discharge valve (18), secondary rotary joint (19), high pressure pipe (20), upper radial-radial bearing (21 ), axial-radial base bearing (22), axial-radial head bearing (23), lower axial-radial bearing (24), primary rotary joint (25), high pressure duct (26), inside the central shaft (27) and toothed pinion (28).

Figure 4. Elevation of the inside of the compressor without the protective cover or the electric motor.

Figure 5. Isometric of the elevation of Figure 4 with the support of the inertia pistons and cylinder (29), open linear bearing (30), lower rotating platform (31), upper rotating platform (32), inertia piston (33) ), shock absorber spring (34), axial flow propellers (35), and cylinder heads (36).

Figure 6. Elevation of a cylinder in a configuration with two inertia pistons with the trace of the sectioning plane of Figure 7.

Figure 7. Plan section of Figure 6 with the grooves of the cylinder (37) and the stump (38).

Figure 8. Elevation section of one of the discs, coupled to the secondary axis (11).

Figure 9. Plan view of the disk (10) of Figure 8.

The ordered list and terminology of the elements included in the description is as follows:

1 Electric motor: 2 Engine support: 3 Central axis: 4 Protective cover: 5 Compressed gas outlet: 6 Primary filter: 7 High pressure tank: 8 Vent hole: 9 Magnetic poles: 10 Disc: 11 Secondary axis: 12 High pressure distributor: 13 Cylinder: 14 Compression piston: 15 Intake chamber: 16 Compression chamber: 17 Intake valve: 18 Discharge valve: 19 Secondary rotary joint: 20 High pressure pipeline: 21 Upper radial-radial bearing : 22 Axial-radial base bearing: 23 Axial-radial head bearing: 24 Lower axial-radial bearing: 25 Primary rotary joint: 26 High pressure duct: 27 Central shaft interior: 28 Toothed pinion: 29 Piston support of inertia and cylinder: 30 Open linear bearing: 31 Lower rotating platform: 32 Upper rotating platform: 33 Inertial piston: 34 Damper spring: 35 Axial flow propeller: 36 Cylinder head: 37 Cylinder groove: 38 Trunnion.

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Detailed exposition of a way of carrying out the invention

We detail how to carry out the invention with permanent magnets for electromagnetic coupling, fixed volumetric displacement and air for the gas to be compressed.

The realization of the invention begins with the manufacture of the high pressure tank (7) in laminated and electro-welded steel sheets in the form of a rectangular section bull. This tank is seated and leveled on a horizontal base and in its hollow geometric center the high-pressure distributor (12), machined in steel and with the exit holes coinciding with the entrance holes to the high-pressure tank, is welded together. The primary rotary joint (25), machined in steel, is fixed to the high-pressure distributor by means of a thread and seal.

The central axis (3) is formed by three sections threaded together. From the bottom-up the lower section reaches up to the lower rotating platform (31), the middle section reaches up to the coupling with the high pressure pipes (20) and the upper section reaches up to its coupling with the electric motor. In the lower section the lower axial-radial bearing (24) is adjusted and the assembly, formed by the lower section of the central axis and the aforementioned bearing, is inserted under pressure in the hollow geometric center of the high-pressure tank on the high pressure distributor. The aforementioned assembly with pressure adjustment simultaneously allows the lower section of the central axis to fit into the primary rotary joint (25). The rotation of this section of the central axis and the lower axial-radial bearing is checked below.

The magnetic poles (9) are machined in two halves, in soft iron. The lower half forms one of the magnetic poles (5) and is machined in the form of a circular crown. The axial flow magnetic masses and permanent magnets, preferably of neodymium or samarium, are fixed on threaded screws. This lower half of the magnetic poles is fixed concentrically with the lower section of the central axis, on the high pressure tank. This fixation is done with threaded screws to the upper wall of said tank. In the center of said lower half of the magnetic poles (9), the toothed pinion (28) is adjusted and its free rotation on its bearing is verified. This toothed pinion is made of steel.

The discs (10) (figures 8 and 9), are manufactured with a flat circular steel core on which two flat circular aluminum crowns are placed on both sides, forming a "sandwich" with the steel core in its center. On the steel of the outer perimeter of the disc (10) the teeth are carved to form a cogwheel, of the same modulus as the cogged cock (28). By means of auxiliary supports the discs are presented in their place, meshed with the toothed pinion, before installing the upper half (N) of the magnetic poles (9). This upper half (N) is fixed by screws through its central part, to the lower half (5).

The middle section of the central axis is machined in steel. The lower end of this middle section is threaded with a tight seal and seal over the lower section of the central shaft. This thread has a direction of rotation inverse to the direction of rotation of the central axis. The lower rotating platform (31) is fixed to the middle section of the central axis by means of a connecting sleeve and captive screws. The secondary shafts (11) are machined in steel. The supports of the inertia and cylinder pistons (29) are manufactured in cast aluminum alloy and with screws, are fixed to the secondary shafts (11). The secondary axle assembly (11) and support of the inertia pistons and cylinder (29) is mounted on the lower rotating platform (31), by means of the axial-radial base bearing (22) that is fixed to said platform. In this assembly, the discs (10), which are presented

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instead by auxiliary mounting parts, they are fixed by screws and cotter pins, to the lower ends of the secondary shafts and the auxiliary mounting parts are removed. The rotation of the disk assembly (10) and secondary axes (11) is checked.

Compression cylinders are made of aluminum alloy with anodized internal heat treatment or similar that ensures high wear resistance and low friction coefficient. The compression piston (14) is machined in steel, of uniform section and on its lateral surface the Teflon sealing rings are mounted. A through hole with thread is machined in the center of the lateral surface of the compression piston and on the same diameter. The compression piston with its Teflon rings is installed inside the cylinder and the assembly is fixed in place on the supports of the inertia and cylinder pistons (29), using threaded prisoners with lost heads. Linear bearings (30), open standard manufacturing are installed in their supports. The inertia pistons (33) are machined in steel or alternatively in bronze alloy with a hole centered and threaded on its lateral surface. The stumps (36) are made of steel, threaded over their entire lateral surface and initially threaded into the threaded holes of the inertia pistons (33) at the depth necessary for the said inertia pistons (33) to adjust in their Linear bearings (30) without hindering the external walls of the compression chambers (16) in this setting. With the inertia pistons (33) in their linear bearings (30), the free spaces in the grooves of the cylinders (37) are used to thread the stumps (36) into the threaded side holes of the compression pistons (14).

The cylinder heads (13) are made of steel, machining the holes for the adjustment and fixing of the intake valves (17), the discharge valves (18) and the support of the damping springs ( 3. 4). The cylinder heads are fixed by means of threaded screws and seat joints to the cylinders. Once fixed, the intake valves (17) and the discharge valves (18) are mounted. These valves are of standard manufacture and with their work curves appropriate to the pressure and type of gas. The damping springs (34) are fixed. It joins in the middle section of the central axis, the upper rotating platform (32) that is fixed to the aforementioned axis by means of connecting bush and screws. The upper axial-radial bearings (23) of the secondary shafts (11) are mounted on this platform and in the bore that channels the compressed gas of the aforementioned shafts, the secondary rotary joints (19) are adjusted. To these secondary rotary joints (19) are threaded, by means of pressure fittings of standard manufacturing, the high pressure pipes (20). The upper section of the central axis is machined in steel with its lower end threaded in the opposite direction to the direction of rotation of said axis, threading said end on the middle section and coupling on the upper section of the central axis, by means of standard union fittings, high pressure pipes (20).

The cover (4) is made of rolled steel sheet with the necessary reinforcements to support the weight of the electric motor (1) and the holes for fixing the primary filters (6) and the upper ventilation. The base of the aforementioned cover is fixed, by means of screws and seat gasket, in the high pressure tank and in its upper closure the supports (2) of the electric motor (1) and of the upper axial-radial bearing (21) are fixed . The aforementioned electric motor is mounted from top to bottom, fitting its shaft with keyway in the machined recess for this purpose, in the upper section of the central shaft (3). Once fitted, the electric motor housing (1) is screwed to its supports. The filters (6) are of standard manufacturing and adapted to the type of filtering that the gas to compress requires. Once assembled, the aforementioned filters, in the lateral holes of the cover, the embodiment of the invention is completed, with the connection of the electric motor (1), to the source of electrical energy.

Industrial application of the invention

It has application in the compression of any type of gas or its mixtures in one or several gaseous and / or liquid phases. For this property it has an easy adaptation for its application in the petrochemical industry.

As an air compressor it can be used in any industrial process that requires compressed air at high or very high pressure and with special relevance in the plastic injection (PET) industry and in naval applications.

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Using membranes for the waterproof closure of compression and intake chambers, it can be used to compress volatile gases such as hydrogen. It allows its adaptation to use it, as a pre-combustion stage, in the jet propulsion engine and circular impulse when using conventional fuel.

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Claims (8)

5 10 fifteen twenty 25 30 35 40 Four. Five fifty 1. Compressor of inertial pistons and rotary cylinders formed by several cylinders (13) rotating on their secondary axes (11), inside which a gas is compressed, by the alternative movement made by pistons (14) installed inside the cylinders . The reciprocating movement of the pistons is produced by their inert masses subjected to a centrifugal force field, combined with the circular translation of the cylinders and pistons and the simultaneous rotation of both. For this, it is characterized by having several cylinders (13) and having a compression chamber (16), an intake chamber (15) for each cylinder and in its central part openings of the cylinder (37) that separate both cameras; having a compression piston (14) and several inertia pistons (33); disposing of stumps (38) that join the compression piston with the inertia pistons; have two cylinder heads (36), incorporating in each cylinder head an intake valve (17) and a discharge valve (18); have damping springs (34) for the inertia pistons (33); having a support for the inertia and cylinder pistons (29) and a secondary shaft (11); have a discharge duct (26) for each cylinder head (36). Provide for each secondary axis a secondary rotary joint (19), a high pressure pipe (20), an axial-radial base bearing (22) and an axial-radial head bearing (23). Have a lower rotating platform (31) and an upper rotating platform (32) fixed to a central axis (3) with a hollow central axis interior (27) and with an upper axial-radial bearing (21) and an axial bearing - lower radial (24) that support said central axis. Have a primary rotary joint (25), a high pressure distributor (12) and a high pressure tank (7) with compressed gas inlets (7); have a cover (4) on which it supports, by means of a motor support (2,) an electric motor (1). Provide, fixed at one of the ends of the secondary shafts (11), discs (10) formed by good electrically conductive materials or alternatively good electrically conductive materials and ferromagnetic materials, serrated in their circular perimeters; have a free-toothed pinion (28) on the central shaft (3) and meshed with the discs (10); have magnetic poles (9), formed by permanent magnets or alternatively by electric coils, with their magnetic fluxes cutting to circular sectors of the discs (10). 2. Compressor of inertial pistons and rotary cylinders, according to claim 1, which supplies a highly volatile compressed gas and for this it is characterized by having elastic membranes or alternatively bellows that close the compression chambers (16) and the intake chambers (fifteen). 3. Compressor of inertial pistons and rotary cylinders, according to claim 1, which supplies a compressed gas free of contaminating particles and for this it is characterized by having primary filters (6) installed in the gas suction circuit, before the valve intake (17) and alternatively have in addition to secondary filters installed in the intake valve itself (17). 4. Compressor of inertial pistons and rotary cylinders, according to claim 1 and which compensates for possible head losses in the suction circuit and improves the cooling of the cylinders that compress the gas and for this it is characterized by installing axial flow propellers ( 35) on the circular perimeter of the lower turntable (31). 5. Compressor of inertial pistons and rotary cylinders, according to claim 1, which installs alternating current electric coils to create the magnetic poles (9) and regulate the speed of rotation of the disks (10) and thereby the volumetric displacement of the compressor and for this it is characterized by having power electric in alternating current to the inductive electric coils of the magnetic poles (9) and of a frequency inverter at the input of said power supply. 6. Compressor of inertial pistons and rotary cylinders, according to claim 1, which installs DC electric coils to create the magnetic poles (9) and regulate the speed of rotation of the disks (10) and with it the volumetric displacement of the compressor and for this it is characterized by having a power supply in direct current for the said electric coils and a variator of intensity in the input of the mentioned feeding. 10 7. Compressor of inertial pistons and rotary cylinders, according to claim 1, which maintains a constant magnetic flux in the magnetic poles (9) and regulates the rotation of the disks (10) and thereby the volumetric displacement of the compressor and for this purpose it is characterized by having permanent magnets in the magnetic poles (9) and 15 have air gap adjustment mechanisms between the magnetic poles (9) and the discs (10). 8. Compressor of inertial pistons and rotary cylinders, according to claim 1, which regulates the compressed gas outlet pressure and is characterized by 20 have a frequency inverter in the power supply to the electric motor (1) of alternating current.